CN216199415U

CN216199415U - Actuator and machine

Info

Publication number: CN216199415U
Application number: CN202122453260.2U
Authority: CN
Inventors: P·P·布赖恩; D·S·贾斯汀; M·正之; K·康博
Original assignee: Caterpillar Inc
Current assignee: Caterpillar Inc
Priority date: 2020-10-16
Filing date: 2021-10-12
Publication date: 2022-04-05
Anticipated expiration: 2031-10-12
Also published as: AU2020102772A4

Abstract

An actuator and machine, the hydraulic ram of the actuator including a tube having a central axially extending bore defined therein and extending between a closed distal end of the tube and an open proximal end of the tube. A stem is slidably mounted within the tube and is slidably supported at the proximal end of the tube by the head seal assembly. The piston is mounted at the distal end of the rod and is retained on the rod by a piston retention assembly attached to the distal end of the rod. A trunnion cap hole for receiving a trunnion pin is defined through the closed distal end of the tube, and a rod eye hole for receiving a rod eye pin is defined through the proximal end of the rod. When the rod and piston are fully retracted into the tube, the retracted inter-pin dimension is defined from the center of the trunnion cap hole to the center of the rod eye hole. The stroke dimension is defined from a first fully retracted position of the piston adjacent the closed distal end of the tube to a second fully extended position of the piston in contact with the head seal assembly at the proximal end of the tube.

Description

Actuator and machine

Technical Field

The present disclosure relates generally to a hydraulic ram for heavy machinery, and more particularly to a hydraulic ram having specific performance dimensions that meet the kinematic, structural, and load requirements of the machinery.

Background

Conventional hydraulic systems on heavy machinery, such as excavators, graders, front end loaders, and dozers, may include a pump that draws low pressure fluid from a tank, pressurizes the fluid, and makes the pressurized fluid available to a plurality of different actuators for use in moving the actuators. The actuators may include hydraulic rams specifically designed to meet various kinematic, structural, and load requirements to move the various structural elements of the machine relative to one another as the machine is used to perform its assigned tasks. For example, one or more hydraulic rams may be specifically designed to handle hydraulic pressures, kinematics, torsional stresses, compressive stresses, tensile stresses, hoop stresses, range of motion, and speed of motion required in operating a particular machine to perform a work task (such as digging, moving earth, lifting a weight, and carrying a weight). In various example devices, the speed of each actuator may be independently controlled by selectively throttling (i.e., restricting) the flow of pressurized fluid from the pump into each actuator. For example, to move a particular actuator at high speed, fluid flow from the pump into the actuator is only slightly restricted (or not restricted at all). Conversely, to move the same actuator or another actuator at a low speed, the restriction to fluid flow is increased. While suitable for many applications, the use of fluid restriction to control actuator speed may result in pressure losses, thereby reducing the overall efficiency of the hydraulic system.

An alternative type of hydraulic system is known as a closed loop hydraulic system. Closed-loop hydraulic systems typically include a pump connected in a closed-loop manner to a single actuator or a pair of actuators operating in series. During operation, the pump draws fluid from one chamber of the actuator and discharges pressurized fluid into an opposite chamber of the same actuator. For example, when the rod of a hydraulic ram is retracted, hydraulic fluid may be pumped into the rod end chamber of the hydraulic ram and drained from the head end chamber on the opposite side of the piston to which the rod in the hydraulic ram is attached, and when the rod is extended, hydraulic fluid may be pumped into the head end chamber and drained from the rod end chamber. To move the actuator at a higher speed, the pump discharges fluid at a faster rate. To move the actuator at a slower speed, the pump discharges fluid at a slower rate. Closed loop hydraulic systems are generally more efficient than conventional hydraulic systems because the speed of the actuator is controlled by pump operation rather than fluid restriction. That is, the pump is controlled to discharge only as much fluid as is required to move the actuator at the desired speed, and no throttling of the fluid is required.

An exemplary closed loop hydraulic system for use in conjunction with one or more hydraulic rams is disclosed in us patent 4,369,625 to Izumi et al, published as 25/1/1983 (the' 625 patent). In the' 625 patent, a multi-actuator meterless hydraulic system having flow combining functionality is described. The hydraulic system includes a swing circuit, a boom circuit, an arm circuit, a bucket circuit, a left travel circuit, and a right travel circuit. Each of the swing, boom, stick and bucket circuits has a pump connected in a closed loop manner to a dedicated hydraulic ram. Further, a first combination valve is connected between the swing circuit and the arm circuit, a second combination valve is connected between the arm circuit and the boom circuit, and a third combination valve is connected between the bucket circuit and the boom circuit. The left and right travel circuits are connected in parallel to the pumps of the bucket and the boom circuit, respectively. In this configuration, any one hydraulic ram may receive pressurized fluid from more than one pump such that its speed is not limited by the capacity of a single pump.

Although an improvement over existing closed-loop hydraulic systems, the closed-loop hydraulic system of the' 625 patent may still be less than optimal. In particular, the connecting loops of the system can only be performed sequentially. In addition, it may be difficult to control the speed and force of the various actuators.

SUMMERY OF THE UTILITY MODEL

The utility model provides an actuator and a machine, which can solve the technical problem that the mutual relation design of the sizes of all parts in the actuator in the prior art cannot optimize and influence the comprehensive performance of the machine.

An actuator configured for actuating a first structural element on a machine relative to a second structural element on the machine, the actuator comprising:

a tube including a central axially extending bore defined therein extending between a closed distal end of the tube and an open proximal end of the tube;

a stem slidably mounted within the tube, the stem being slidably supported at a proximal end of the tube by a head seal assembly;

a piston mounted at a distal end of the rod;

a piston retention assembly attached to the distal end of the rod and configured to retain the piston at the distal end of the rod between the piston retention assembly and a bushing mounted on a reduced diameter portion of the distal end of the rod;

a trunnion cap hole defined through the closed distal end of the tube and configured to receive a trunnion pin adapted to pivotally connect the distal end of the tube to the first structural element of the machine; and

a rod eye defined through a proximal end of the rod and configured for receiving a rod eye pin adapted to pivotally connect the proximal end of the rod to the second structural element of the machine; wherein

A retracted inter-pin dimension from the center of the trunnion cap hole to the center of the rod eye hole equal to 1255mm ± 2.0 mm when the rod and the piston are fully retracted into the tube such that the distal end of the rod is at the closed distal end of the tube;

a stroke dimension from a first fully retracted position of the piston adjacent the closed distal end of the tube to a second fully extended position of the piston in contact with the head seal assembly at the proximal end of the tube is equal to 709mm ± 2.0 mm;

the diameter of the rod eye hole is equal to 130mm +/-0.5 mm;

the diameter of the trunnion cap hole is equal to 120 mm +/-0.5 mm;

the diameter of the central axially extending bore of the tube is equal to 170mm ± 0.5 mm;

the diameter of the rod is equal to 100mm plus or minus 0.5 mm.

The pressure of the hydraulic fluid supplied to the actuator is 35,000 kPa + -3,500 kPa.

The machine is an excavator, the first structural element comprises a body of the excavator, and the second structural element comprises a boom of the excavator.

Further comprising a damping assembly disposed at the closed distal end of the tube, adjacent the distal end of the rod when the rod is fully retracted into the tube.

The damping assembly projects axially from a radially intermediate portion of the closed distal end of the tube.

The damping assembly is configured to be received within a mating blind hole formed in the distal end of the rod when the rod is fully retracted into the tube.

Further comprising a damping assembly retained within a blind bore in the distal end of the rod, the damping assembly configured to enter a radially centered axial bore in the closed distal end of the tube when the rod is fully retracted into the tube.

Also included is an axial relief hole extending into the closed distal end of the tube, extending parallel to and offset from a central axis of the tube, penetrating into the closed distal end of the tube, and intersecting with a radially oriented relief hole extending between a pressure relief chamber defined in the distal end of the tube and an outer circumferential periphery of the tube.

The head seal assembly is bolted to a rod end boss disposed at the proximal end of the tube.

A machine comprising a plurality of structural elements and a plurality of hydraulic actuators, each hydraulic actuator interconnecting two of the structural elements,

wherein each hydraulic actuator is configured to actuate a first structural element on the machine relative to a second structural element on the machine, each hydraulic actuator comprising:

a piston mounted at a distal end of the rod;

A retraction interline dimension from the center of the trunnion cap hole to the center of the rod eye hole equal to 1255mm ± 2.0 mm when the rod and the piston are fully retracted into the tube such that the distal end of the rod is at the closed distal end of the tube;

the diameter of the rod eye hole is equal to 130mm +/-0.5 mm;

the diameter of the trunnion cap hole is equal to 120 mm +/-0.5 mm;

the diameter of the rod is equal to 100mm plus or minus 0.5 mm; and is

In one aspect, the present disclosure is directed to an actuator configured to actuate a first structural element of a machine relative to a second structural element of the machine. The actuator may include a tube including a central axially extending bore defined therein extending between a closed distal end of the tube and an open proximal end of the tube. A stem is slidably mounted within the tube, the stem being slidably supported at a proximal end of the tube by a head seal assembly. A piston may be mounted at a distal end of the rod, and a piston retention assembly may be attached to the distal end of the rod and may be configured to retain the piston at the distal end of the rod between the piston retention assembly and a bushing mounted on a reduced diameter portion of the distal end of the rod. A trunnion cap hole may be defined through the closed distal end of the tube and configured to receive a trunnion pin adapted to pivotally connect the distal end of the tube to the first structural element of the machine. A rod eye may be defined through the proximal end of the rod and configured for receiving a rod eye pin adapted to pivotally connect the proximal end of the rod to the second structural element of the machine.

In another aspect, the utility model relates to a machine comprising a plurality of structural elements and a plurality of hydraulic actuators each interconnecting two of the two structural elements, wherein each hydraulic actuator is configured to actuate a first structural element on the machine relative to a second structural element on the machine. Each hydraulic actuator may include a tube having a central axially extending bore defined therein extending between a closed distal end of the tube and an open proximal end of the tube. A stem is slidably mounted within the tube, the stem being slidably supported at a proximal end of the tube by a head seal assembly. A piston may be mounted at a distal end of the rod, and a piston retention assembly may be attached to the distal end of the rod and may be configured to retain the piston at the distal end of the rod between the piston retention assembly and a bushing mounted on a reduced diameter portion of the distal end of the rod. A trunnion cap hole may be defined through the closed distal end of the tube and configured to receive a trunnion pin adapted to pivotally connect the distal end of the tube to the first structural element of the machine. A rod eye may be defined through the proximal end of the rod and configured for receiving a rod eye pin adapted to pivotally connect the proximal end of the rod to the second structural element of the machine.

In yet another aspect, the present disclosure is directed to a hydraulic ram configured to actuate a first structural element on a machine relative to a second structural element on the machine. The hydraulic ram may include a tube including a central axially extending bore defined therein extending between a closed distal end of the tube and an open proximal end of the tube. A stem is slidably mounted within the tube, the stem being slidably supported at a proximal end of the tube by a head seal assembly. A piston may be mounted at a distal end of the rod, and a piston retention assembly may be attached to the distal end of the rod and may be configured to retain the piston at the distal end of the rod between the piston retention assembly and a bushing mounted on a reduced diameter portion of the distal end of the rod. A trunnion cap hole may be defined through the closed distal end of the tube and configured to receive a trunnion pin adapted to pivotally connect the distal end of the tube to the first structural element of the machine. A rod eye may be defined through the proximal end of the rod and configured for receiving a rod eye pin adapted to pivotally connect the proximal end of the rod to the second structural element of the machine.

The present invention provides an actuator and machine, the hydraulic ram of which is designed to have a range of specific performance dimensions, the range being determined by a combination of extensive analysis including the application of physics-based equations, finite element analysis and other computational analysis that take into account kinematic and structural stresses that will be imposed on the ram during use, and empirical and other customer-centric data that is intended to meet specific operational requirements and address one or more technical problems of the prior art and/or other technical problems of the prior art. These technical problems include component stresses, operating characteristics, fatigue life, and overall inefficiency of the hydraulic system.

Furthermore, the hydraulic ram is preferably designed to have a particular range of dimensions for stroke, length between pins at full retraction, diameter of the rod end pin, and diameter of the trunnion pin at the head end of the ram, depending on the particular machine and load application in which the hydraulic ram will be used.

Additionally, hydraulic rams for heavy machinery may benefit from the combination of the specific performance dimensions disclosed in this disclosure and the features such as the damping device and head seal that form a technical solution that improves the operating characteristics, fatigue life, and overall performance under extreme conditions.

The values and relationships between the hydraulic rams of the present invention, such as stroke size, inter-pin size, trunnion cap hole and trunnion pin diameters, and rod eye pin diameters, are determined by extensive data analysis, including empirical data and other customer-centric data. The data analysis includes the application of physics-based equations, finite element analysis, and other computational analysis that takes into account the supply hydraulic fluid pressure, kinematics, and structural stresses that will be exerted on the hydraulic cylinder during use. The numerical value obtained by the method can meet the operation requirement and solve one or more technical problems caused by the fact that the numerical value cannot be optimized in the prior art.

It can be seen that the disclosed embodiments of the present invention may provide improved energy usage and savings. In addition, the ability to combine fluid flow from different circuits to meet the demands of each actuator may allow for a reduction in the number of pumps required within the hydraulic system and/or the size and capacity of these pumps. These reductions may reduce pump losses, increase overall efficiency, improve the volume of the hydraulic system, and/or reduce the cost of the hydraulic system.

Drawings

FIG. 1 is an illustration of an exemplary disclosed machine.

FIG. 2 is an illustration of an exemplary disclosed hydraulic ram that may be used as an actuator on the machine of FIG. 1.

FIG. 3 is a cross-sectional view of the disclosed example hydraulic ram of FIG. 2.

FIG. 4 is an enlarged view of portion 4 of the hydraulic ram of FIG. 3 showing the piston retaining assembly at the first end of the piston rod of the hydraulic ram; and is

FIG. 5 is an enlarged view of the portion of the hydraulic ram of FIG. 3 identified by reference number 5, showing the head seal configuration at the piston rod end of the hydraulic ram.

Detailed Description

FIG. 1 illustrates an exemplary machine 10 having multiple systems and components that cooperate to accomplish a work task. Machine 10 may embody a fixed or mobile machine that performs some type of operation associated with an industry such as mining, construction, farming, transportation, or another industry known in the art. For example, machine 10 may be an earth moving machine such as an excavator (shown in FIG. 1), a dozer, a front end loader, a backhoe, a motor grader, a dump truck, or any other earth moving machine or other heavy machinery. Machine 10 may include an implement system 12 configured to move a work tool 14, a drive system 16 for propelling machine 10, a power source 18 that provides power to implement system 12 and drive system 16, and an operator station 20 positioned to manually control implement system 12, drive system 16, and/or power source 18.

Implement system 12 may include a linkage structure acted on by fluid actuators to move work tool 14. Specifically, implement system 12 may include a boom 22 that pivots vertically about a horizontal axis (not shown) relative to a work surface 24 via a pair of adjacent, double-acting, hydraulic rams 26 (shown only in fig. 1). Implement system 12 may also include a stick 28, with stick 28 being vertically pivoted about a horizontal axis 30 by a single, double-acting, hydraulic ram 32. Implement system 12 may also include a single, dual-acting hydraulic ram 34, with dual-acting hydraulic ram 34 operatively connected between stick 28 and work tool 14 to pivot work tool 14 vertically about a horizontal pivot axis 36. In the disclosed embodiment, hydraulic ram 34 is connected to a portion of stick 28 at a head end 34A and to work tool 14 at an opposite rod end 34B via a power link 37. Boom 22 is pivotally connected to a body 38 of machine 10. The body 38 is pivotably connected to the chassis 39 and is movable about a vertical axis 41 by a hydraulic swing motor 43. Stick 28 may pivotally connect boom 22 to work tool 14 via axis 30 and axis 36. It is contemplated that a different number and/or configuration of actuators may alternatively be included within implement system 12, in the same or different manners as described above, if desired.

Many different work tools 14 may be attached to a single machine 10 and operator controllable. Work tool 14 may include any device for performing a particular task such as, for example, a bucket, a fork arrangement, a blade, a shovel, a ripper, a dump bed, a broom, a snow blower, a propelling device, a cutting device, a grasping device, or any other task-performing device known in the art. Although connected to pivot in a vertical direction and swing in a horizontal direction with respect to body 38 of machine 10 in the embodiment of fig. 1, work tool 14 may alternatively or additionally rotate, slide, open and close, or move in any other manner known in the art. Further, while the exemplary embodiment in FIG. 1 illustrates a hydraulic ram configured for actuating structural elements of an excavator including a boom, an arm, and a bucket, one of ordinary skill in the art will recognize that the disclosed embodiments of hydraulic rams may be interconnected between other structural elements on different machines to actuate any structural element of a machine relative to another structural element of the machine while performing a particular task for which the machine is designed.

Drive system 16 may include one or more traction devices that provide power to propel machine 10. In the disclosed example, drive system 16 includes a left track 40L located on one side of machine 10 and a right track 40R located on an opposite side of machine 10. Left track 40L may be driven by a left travel motor 42L, while right track 40R may be driven by a right travel motor 42R. It is contemplated that drive system 16 may alternatively include traction devices other than tracks, such as wheels, belts, or other known traction devices. Machine 10 may be steered by generating a speed and/or rotational direction difference between left and

right travel motors

42L, 42R, while straight travel may be traveled by generating substantially equal output speeds and rotational directions from left and

right travel motors

42L, 42R.

Power source 18 may embody an engine such as, for example, a diesel engine, a gasoline engine, a gaseous fuel-powered engine, or any other type of combustion engine known in the art. It is contemplated that power source 18 may alternatively embody a non-combustion power source such as, for example, a fuel cell, a power storage device, a tethered motor, or another power source known in the art. Power source 18 may produce a mechanical or electrical power output that may then be converted to hydraulic power to move

hydraulic rams

26, 32, 34 and left and

right travel motors

42L, 42R, and swing motor 43.

Operator station 20 may include devices that receive input from a machine operator indicative of a desired machine maneuver. Specifically, operator station 20 may include one or more operator interface devices 46, such as joysticks, steering wheels, or pedals, located proximate an operator seat (not shown). Operator interface device 46 may initiate movement of machine 10, such as travel and/or tool movement, by generating displacement signals indicative of a desired machine maneuver. As the operator moves the interface device 46, the operator may operate the corresponding machine movement in a desired direction, at a desired speed, and/or with a desired force.

As shown in fig. 2 and 3,

hydraulic rams

26, 32, 34 may each include a tube 322 and a piston 420 disposed within tube 322 to form a first chamber 352 and an opposing second chamber 354. The first chamber 352 may be considered a head end chamber and the second chamber 354 may be considered a rod end chamber of the

hydraulic rams

26, 32, 34. The tube 322 may include a central axially extending bore 326, the central axially extending bore 326 being defined in the tube 322, extending between the closed distal end 342 of the tube 322 and the open proximal end of the tube 322. The central axially extending bore 326 of the tube 322 may partially define a first or head end chamber 352 and an opposing second or rod end chamber 354, and may further include a diameter 328, the diameter 328 extending substantially along a length of the interior of the tube 322 that is coaxially aligned with a central axis of the tube 322 and the rod 332. The rod 332 may further include an outer diameter 334, the outer diameter 334 being coaxially aligned with the central axis of the tube 322 and extending from the piston 420 and piston retaining assembly 430 to the proximal end 344 of the rod 332 substantially along the length of the exterior of the rod 332. A radial clearance, offset, or gap between the outer diameter 334 of the stem 332 and the diameter 328 of the central axially extending bore 326 of the tube 322 may partially define a second or stem end chamber 354. The exemplary embodiment of piston 420 and piston retaining assembly 430 shown in fig. 3 and 4 may be disposed at the distal end of rod 332. The piston 420 may be retained between the piston retention assembly 430 and the bushing 410 at the distal end of the rod 332, as shown in fig. 4. Bushing 410 may rest on a reduced diameter shoulder at the distal end of rod 332. In an alternative embodiment, piston retaining assembly 430 may be threadably engaged or press-fit onto the distal end of rod 332, and bushing 410 may be omitted or replaced by a resilient shock absorbing member configured to assist in reducing vibrations and absorbing any shock that may occur as piston 420 strikes the closed distal end 342 of tube 322 at the bottom of each stroke. The piston 420 may also include a plurality of annular seals 422 spaced along the outer periphery of the piston 420 and forming a slidable seal between the piston 420 and the inner circumferential surface of the tube 322 as the rod 332 and piston 420 reciprocate within the tube 322 due to changes in the pressure and/or flow rate of hydraulic fluid supplied to and released from the head end chamber 352 and the rod end chamber 354.

In some exemplary embodiments, a damping assembly 440 may be disposed at the closed distal end 342 of the tube 322 adjacent the distal end of the piston rod 332 at the bottom of its stroke, as shown in fig. 3 and 4. Additionally, a piston retention assembly 430 may be threadably attached or otherwise secured to the distal end of the piston rod 332, abutting against one axial end of the piston 420, and received at the bottom of each stroke in a radially inwardly extending rib 325 formed near the closed distal end 342 of the tube 322. As the piston 420 and piston retention assembly 430 approach the closed distal end 342 of the tube 322 at the bottom of each stroke, hydraulic fluid trapped in the head end chamber 352 may be forced through the gap between the ribs 325 and the outer peripheral surface of the piston retention assembly 430, thereby promoting a damping effect that slows the travel of the piston rod and piston before the piston rod 332 and piston 420 collide with the closed distal end 342 of the tube 322. Damping assembly 440 may also be configured with an internal passage designed to restrict the flow of hydraulic fluid escaping from head chamber 352 at the bottom of each stroke of piston 420 and rod 332.

Damping assembly 440 may protrude axially from a radially central location of closed distal end 342 of tube 322, and may be configured to be received within a mating blind hole formed in the distal end of rod 332 at the bottom of the rod's stroke. Whenever the rod 332, piston retaining assembly 430, and piston 420 approach the closed distal end 342 of tube 322, the damping assembly 440 may enter a blind hole in the distal end of rod 332. In an alternative embodiment, damping assembly 440 may be retained within a blind hole in the distal end of rod 332 with one or more annular seals 460 interposed between an outer peripheral surface of damping assembly 440 and an inner peripheral surface of the blind hole in the distal end of rod 332. Damping assembly 440 may be configured to enter a radially centered axial bore in closed distal end 342 of tube 322 at the bottom of each stroke. An axially oriented release hole 451 may also be formed in the closed distal end 342 of the tube 322 extending parallel to and offset from the central axis of the tube 322 and the rod 332, wherein the axially oriented release hole 451 penetrates into the closed distal end 342 of the tube 322 and intersects with a radially oriented release hole 450, the radially oriented release hole 450 extending between a relief chamber 452 formed in the distal end 342 of the tube 322 and the outer circumferential periphery of the tube 322. As piston 420, piston retention assembly 430, and damping assembly 440 approach closed distal end 342 of tube 322 at the bottom of the stroke (or as piston 420 and piston retention assembly 430 approach damping assembly 440 protruding from distal end 342), damping assembly 440 may be configured to enter a blind hole in the distal end of rod 332. Fluid in head-end chamber 352 may be forced through axially-oriented relief holes 451, into pressure relief chambers 452, and out of radially-oriented relief holes 450. The damping assembly 440 may also include a central axially oriented release hole 446 and a plurality of radially extending and axially spaced

channels

442 and 444 that penetrate from the central axially oriented release hole 446 to the periphery of the damping assembly 440. The central axially-oriented release hole 446 and the radially-extending

channels

442 and 444 in the damping assembly 440 may be configured to assist in adjusting the amount and flow rate of hydraulic fluid that may escape from the head-end chamber 352 as the piston 420 and piston retaining assembly 430 approach the closed distal end 342 of the tube 322 at the bottom of the stroke, thus serving to adjust the damping effect and prevent the rod 332, piston 420, and piston retaining assembly 430 from forcefully striking the bottom of the closed distal end 342 of the tube 322.

Head end chamber 352 and rod end chamber 354 may each be selectively supplied with pressurized fluid and drained of the pressurized fluid to displace piston 420 within tube 322, thereby changing the effective length of

hydraulic rams

26, 32, 34 and moving work tool 14 (see fig. 1), or otherwise moving one structural component of machine 10 to which one of proximal end 344 of piston rod 332 or distal end 342 of tube 322 is pivotally connected relative to another structural component of machine 10. The flow rate of fluid into and out of

chambers

352, 354 may be related to the translational velocity of

hydraulic rams

26, 32, 34, while the pressure differential between

chambers

352, 354 may be related to the force applied by

hydraulic rams

26, 32, 34 to the associated linkage structure of implement system 12.

As shown in fig. 3 and 5, the proximal end 344 of the stem 332 may pass through a head seal assembly 520, the head seal assembly 520 being bolted or otherwise attached to the stem end boss 324 at the proximal end of the tube 322. The head seal assembly 520 may include a plurality of axially spaced seals 522 along the inner circumferential periphery of the head seal assembly 520, the seals 522 configured to form a slidable seal with the periphery of the proximal end 344 of the stem 332. A plurality of bolts 327 may secure the head seal assembly 520 to the rod end boss 324, wherein a portion of the head seal assembly 520 extends at least partially radially inward from the rod end boss 324 of the tube 322 and is configured to radially support the proximal end 344 of the rod 332 as the rod 332 and piston 420 reciprocate relative to the tube 322. Proximal end 344 of rod 332 may include a rod eye of diameter 252 extending through rod 332 orthogonal to the central axis of rod 332 and configured to receive a rod eye pin for pivotally attaching proximal end 344 of rod 332 to a first structural element of machine 10, such as a rod eye pin, which pivotally connects rod end 34B of hydraulic ram 34 to work implement 14 via power link 37, as shown in fig. 1. The distal end 342 of tube 322 may similarly include a trunnion cap hole 242 in diameter that extends through the distal end 342 of tube 322 normal to the central axis of rod 332 and tube 322 and is configured to receive a trunnion pin that pivotally attaches the distal end 342 of tube 322 to a second structural element of machine 10, such as a trunnion pin, that is configured to pivotally connect the head end 34A of hydraulic ram 34 to a portion of stick 28, as shown in fig. 1.

The diameter 252 of the rod eye extending through proximal end 344 of rod 332, and thus the rod eye pin configured for pivotally connecting rod 332 of each hydraulic ram to a structural element of machine 10, and the diameter 242 of the trunnion cap hole extending through distal end 342 of tube 322, and thus the diameter of the trunnion pin configured for pivotally connecting tube 322 of each hydraulic ram to another structural element of machine 10, are determined based at least in part on the size of the structural elements of machine 10 to which the pins are pivotally attached, and the loads and structural stresses to which these elements are subjected during operation, such as shear stresses, torsional stresses, compressive stresses, and tensile stresses that would be subjected under load during actuation of each hydraulic ram. The inter-pin dimension 132 of each hydraulic cylinder shown in fig. 2 is determined based at least in part on the size, range of motion, work load, and structural interrelationships of the structural elements of the particular machine, such as boom 22, stick 28, and work tool 14 of each machine 10. The stroke 222 of each hydraulic ram shown in fig. 3 is similarly determined based at least in part on the size, range of motion, work load, and structural interrelationships of the structural elements of each machine 10. The rod 332 and piston 420 are shown fully retracted into the tube 322 in fig. 3, with the stroke 222 being determined by the distance from such fully retracted position when the piston 420 bottoms out at the closed distal end 342 of the tube 322 to the fully extended position of the rod 332 when the piston 420 contacts the head seal assembly 520 bolted to the rod end boss 324 of the tube 322. In one embodiment, one or more of inter-pin dimension 132, stroke 222, rod eye diameter 252, and trunnion cap diameter 242, as well as various additional disclosed dimensions, characteristics, and features of each

hydraulic ram

26, 32, 34, may be determined based at least in part on system pressures specific to

hydraulic rams

26, 32, 34, as further explained herein.

As with

hydraulic rams

26, 32, 34, left travel motor 42L, right travel motor 42R, and swing motor 43 may each be driven by a hydraulic differential. In particular, each of these motors may include first and second chambers (not shown) located on either side of a corresponding pumping mechanism, such as an impeller, plunger, or series of pistons (not shown). When the first chamber is filled with pressurized fluid and the second chamber is drained of fluid, the pumping mechanism may be caused to move or rotate in a first direction. Conversely, when the first chamber is drained of fluid and the second chamber is filled with pressurized fluid, the pumping mechanism may be caused to move or rotate in the opposite direction. The flow rate of fluid into and out of the first and second chambers may determine the output speed of the respective motor, while the pressure differential across the pumping mechanism may determine the output torque. The displacement of left travel motor 42L, right travel motor 42R, and/or swing motor 43 may be variable and may be of an eccentric type, if desired. In an alternative embodiment, the motors may be provided with controls and devices to support the load when changing the direction of displacement, such that the speed and/or torque output of each motor may be independently adjusted for a given flow rate and/or pressure of the supplied fluid.

Machine 10 may include a hydraulic system (not shown) having multiple circuits that drive the aforementioned fluid actuators (hydraulic rams) to move work tool 14 (referring to fig. 1) and machine 10. Specifically, the hydraulic system may include, among other things and as one exemplary embodiment, a first circuit, a second circuit, a third circuit, a fourth circuit, and a fifth circuit. In an exemplary embodiment, the first circuit may be primarily associated with hydraulic rams 32 and right travel motor 42R. The second circuit may be primarily associated with the swing motor 43. The third circuit may be primarily associated with hydraulic rams 34. The fourth circuit may be primarily associated with left travel motor 42L and hydraulic ram 26. The fifth circuit may be primarily associated with an auxiliary actuator, such as an auxiliary motor or cylinder (not shown) directly associated with work tool 14. It is contemplated that additional and/or different configurations of circuits may be included within the exemplary hydraulic system, if desired, such as, for example, an oil-filled circuit associated with each of the first-fifth circuits, and/or a separate circuit associated with hydraulic rams 26 or 34.

In the disclosed embodiments, each of the circuits may be similar and include a plurality of interconnected and cooperating fluid components that facilitate use and control of an associated actuator. For example, each of the circuits may include a pump fluidly connected to its associated actuator via a closed circuit formed by the left and right side channels. In particular, each of the circuits may include a common left pump passage, a common right pump passage, a left actuator passage for each actuator, and a right actuator passage for each actuator. In circuits with linear actuators (e.g., hydraulic rams 26, 32, or 34), the left and right actuator passages are commonly referred to as head-end passages and rod-end passages, respectively. Within each circuit, the corresponding pump may be connected to its associated actuator via a combination of left and right pump channels and actuator channels.

To rotate the rotary actuator (e.g., left travel motor 42L, right travel motor 42R, swing and/or auxiliary motor 43) in a first direction, the left actuator channel of a particular circuit may be filled with fluid pressurized by the pump, while the corresponding right actuator channel may be filled with fluid exiting the rotary actuator. To reverse the direction of the rotary actuator, the right actuator channel may be filled with fluid pressurized by the pump, while the left actuator channel may be filled with fluid exiting the rotary actuator.

To retract a linear actuator (e.g., hydraulic rams 26, 32, or 34), the right actuator channel of a particular circuit may be filled with fluid pressurized by the pump, while the corresponding left actuator channel may be filled with fluid returned by the linear actuator. Conversely, to extend the rotary actuator, the left actuator channel may be filled with fluid pressurized by pump 66, while the right actuator channel may be filled with fluid exiting the linear actuator.

Each pump may have variable displacement and be controlled to draw fluid from its associated actuator and discharge fluid back to the actuator in a single direction at a specified high pressure. That is, the pump may include a stroke adjustment mechanism, such as a swash plate, the position of which is hydro-mechanically adjusted based on, among other things, the desired speed of the actuator, thereby changing the output (e.g., discharge rate) of the pump. The displacement of the pump may be adjusted from a zero displacement position at which substantially no fluid is discharged from the pump to a maximum displacement position at which fluid is discharged from the pump at a maximum rate to the right pump passage. The pump may be drivably connected to power source 18 of machine 10 by, for example, a countershaft, a belt, or in other suitable manners. Alternatively, the pump may be indirectly connected to power source 18 via a torque converter, a gearbox, an electrical circuit, or in any other manner known in the art. It is contemplated that the pumps of the different circuits may be connected to power source 18 in series (e.g., via the same shaft) or in parallel (via a gear train), if desired.

A pump configured to provide pressurized hydraulic fluid to the hydraulic actuator may also be selectively used as a motor. More specifically, when the associated actuator is operating in an overrun condition, the rise in pressure of fluid discharged from the actuator may be higher than the output pressure of the corresponding pump. In this case, the high pressure of the actuator fluid directed back through the pump may be used to drive the pump to rotate with or without the assistance of power source 18. In some cases, the pump may even be capable of applying energy to power source 18, thereby increasing the efficiency and/or capacity of power source 18.

Each of

hydraulic rams

26, 32, 34 may receive hydraulic fluid pressurized to a system pressure. The system pressure of the hydraulic fluid supplied to each of

hydraulic rams

26, 32, 34 may be determined in conjunction with the link calibration and the digging force for each particular model and/or type of work machine on which the hydraulic rams are mounted. The system pressure may fluctuate during operation of the machine 10, where pressure spikes may be a function of the connecting rod standard and the particular application in which the machine is used. The link criteria may include the various characteristics, features and dimensions of each respective

hydraulic ram

26, 32, 34 as disclosed herein, modified according to a desired safety factor designed to accommodate system pressure spikes and other variable attributes and operating characteristics that may affect the rams during machine operation. The link criteria may include one or more of: the inter-pin dimension 132, the stroke 222, the rod eye diameter 252, the trunnion cap hole diameter 242, the diameter 328 of the central axially extending bore 326 of the tube 322, and the outer diameter 334 of the rod 332. These characteristics, features and dimensions may be directly and functionally related to, and may be established based on, the system pressure of the hydraulic fluid supplied to each respective

hydraulic ram

26, 32, 34, which may result in improved performance thereof. In an exemplary embodiment, diameter 328 of central axially extending bore 326 of tube 322 and outer diameter 334 of rod 332 may each be sized to have a system pressure based at least in part on inter-pin dimension 132, stroke 222, rod eye diameter 252, trunnion cap bore diameter 242, and

hydraulic rams

26, 32, 34. Specifically and in one example, diameter 328 of central axially extending bore 326 of tube 322 and outer diameter 334 of rod 332 may be designed such that a particular system pressure within one or more of head end chamber 352 and rod end chamber 354 results in a desired actuation of the hydraulic ram. The desired actuation of the hydraulic ram may include extending rod 332 from tube 322, retracting rod 332 into tube 322, or maintaining rod 332 in any of a number of particular positions relative to tube 322. The selection of the above-discussed dimensions and system pressures for each hydraulic ram in accordance with various embodiments of the present disclosure may result in the actuation of each respective

hydraulic ram

26, 32, 34 such that the connections at the rod eye diameter 252 and the trunnion cap hole diameter 242 move each of the associated structural elements of the particular machine (such as the boom 22, stick 28, and work tool 14) to desired positions at particular speeds and/or accelerations to achieve an overall performance improvement and enhancement of the machine 10.

In one of the following exemplary embodiments of a hydraulic cylinder according to the present disclosure (such as a hydraulic cylinder adapted for use as hydraulic cylinder 32 for actuating boom 28 relative to boom 22), inter-pin dimension 132 of the hydraulic cylinder may be equal to XXXX mm ± XX mm when rod 332, piston retention assembly 430, and piston 420 bottom out at closed distal end 342 of tube 322 are fully retracted. The stroke 222 for the example stick cylinder may be equal to XXXX mm + -XX mm. Rod eye diameter 252 may be equal to XXX mm + -XX mm. The trunnion cap hole diameter 242 may be equal to XXX mm + -XX mm. The diameter 328 of the central axially extending bore 326 of the pipe 322 of the example stick cylinder may be equal to XXXX mm + -XX mm, and the outer diameter 334 of the rod 332 of the example stick cylinder may be equal to XXXX mm + -XX mm. The system pressure of the hydraulic fluid supplied to the example stick cylinder may be equal to XXXX kPa ± XX kPa. The disclosed size ranges are determined for a particular machine based on one or more of: physics-based equations, finite element analysis, empirical evidence, and other data computational analysis that takes into account the following factors: such as kinematic interrelationships between the boom and the stick on the machine, the range of motion of the corresponding structural components, the loads to which the hydraulic rams will be subjected during operation of machine 10, the expected fatigue life, hydraulic fluid pressures, and mechanical safety factors. In one example, one or more of the disclosed ranges of inter-pin dimension 132, stroke 222, rod eye diameter 252, trunnion cap hole diameter 242, diameter 328 of tube 322 central axially extending hole 326, and outer diameter 334 of rod 332 of this example arm cylinder embodiment may be directly and functionally associated with and may be established based on the presently disclosed hydraulic cylinder 32 for an arm 28 having an actuation system pressure of XXXX, which may result in improved and enhanced overall performance in accordance with any one or more of the disclosed embodiments of the utility model.

In another of the following exemplary embodiments of a hydraulic cylinder according to the present disclosure (such as a hydraulic cylinder adapted for use as hydraulic cylinder 26 for actuating boom 22), inter-pin dimension 132 of the hydraulic cylinder may be equal to XXXX mm ± XX mm when rod 332, piston retaining assembly 430, and piston 420 bottom out at closed distal end 342 of tube 322 are fully retracted. The stroke 222 for the example boom cylinder may be equal to XXXX mm + -XX mm. Rod eye diameter 252 may be equal to XXX mm + -XX mm. The trunnion cap hole diameter 242 may be equal to XXX mm + -XX mm. The diameter 328 of the central axially extending bore 326 of the example boom cylinder tube 322 may be equal to XXXX mm + -XX mm, and the outer diameter 334 of the example boom cylinder rod 332 may be equal to XXXXXX mm + -XX mm. The system pressure of the example boom cylinder may be equal to XXXX kPa ± XX kPa. The disclosed size ranges are determined for a particular machine based on one or more of: physics-based equations, finite element analysis, empirical evidence, and other data computational analysis that takes into account the following factors: such as the kinematic interrelationship between the boom and body of the machine, the range of motion of the corresponding structural components, the loads to which the hydraulic rams will be subjected during operation of machine 10, the desired fatigue life, hydraulic fluid pressures, and mechanical safety factors. In one example, one or more of the disclosed ranges of inter-pin dimension 132, stroke 222, rod eye diameter 252, trunnion cap hole diameter 242, diameter 328 of central axially extending bore 326 of tube 322, and outer diameter 334 of rod 332 of the present embodiment of the example boom cylinder may be directly and functionally associated with and established based on the presently disclosed hydraulic cylinder 26 for actuation of boom 22 at system pressure XXXX, which may result in improved and enhanced overall performance in accordance with any one or more of the disclosed embodiments of the utility model.

In yet another of the following exemplary embodiments of a hydraulic ram in accordance with the present disclosure (such as a hydraulic ram adapted for use as hydraulic ram 34 for actuating bucket 14 relative to stick 28), inter-pin dimension 132 of the hydraulic ram may be equal to XXXX mm ± XX mm when rod 332, piston retention assembly 430, and piston 420 bottom out at closed distal end 342 of tube 322 are fully retracted. The stroke 222 for the exemplary bucket cylinder may be equal to XXXX mm + -XX mm. Rod eye diameter 252 may be equal to XXX mm + -XX mm. The trunnion cap hole diameter 242 may be equal to XXX mm + -XX mm. The diameter 328 of the central axially extending bore 326 of the tube 322 of the example bucket cylinder may be equal to XXXX mm + -XX mm, and the outer diameter 334 of the rod 332 of the example bucket cylinder may be equal to XXXX mm + -XX mm. The system pressure of the exemplary bucket cylinder may be equal to XXXX kPa ± XX kPa. The disclosed size ranges are determined for a particular machine based on one or more of: physics-based equations, finite element analysis, empirical evidence, and other data computational analysis that takes into account the following factors: such as kinematic interrelationships between the stick, interconnecting links and bucket or other work tool of machine 10, the range of motion of the respective structural components, the loads to which hydraulic rams will be subjected during operation of machine 10, expected fatigue life, hydraulic fluid pressures, and mechanical safety factors. In one example, and one or more of the disclosed ranges of inter-pin dimension 132, stroke 222, rod eye diameter 252, trunnion cap hole diameter 242, diameter 328 of tube 322 center axially extending hole 326, outer diameter 334 of rod 332 of the present embodiment of the example bucket cylinder may be directly and functionally associated with and may be established based on the presently disclosed hydraulic rams 34 for actuating bucket 14 relative to stick 28 at system pressure XXXX, which may result in improved overall performance in accordance with any one or more of the disclosed embodiments of the present invention.

The above XXXX represents a four-digit number, and the above XX represents a two-digit number. 568LL BOOM hydraulic Cylinder (568 LL BOOM Cylinder) in another exemplary embodiment of a hydraulic Cylinder according to the present disclosure, such as a hydraulic Cylinder adapted for use as hydraulic Cylinder 26 for actuating BOOM 22, when rod 332, piston retention assembly 430, and piston 420 bottom out at closed distal end 342 of tube 322 to fully retract, inter-pin dimension 132 of the hydraulic Cylinder may be equal to 2000 mm 2.0 mm. The stroke 222 for the exemplary boom cylinder may be equal to 1345 mm 2.0 mm. The rod eye diameter 252 may be equal to 110 mm ± 0.5 mm. The trunnion cap hole diameter 242 may be equal to 100mm + -0.5 mm. The diameter 328 of the central axially extending bore 326 of the example boom cylinder tube 322 may be equal to 170mm 0.5 mm and the outer diameter 334 of the example boom cylinder rod 332 may be equal to 110 mm 0.5 mm. The system fluid pressure of the example boom cylinder may be equal to 35,000 kPa ± 3500 kPa. The disclosed size ranges are determined for a particular machine based on one or more of: physics-based equations, finite element analysis, empirical evidence, and other data computational analysis that takes into account the following factors: such as the kinematic interrelationship between the boom and body of the machine, the range of motion of the corresponding structural components, the loads to which the hydraulic rams will be subjected during operation of machine 10, the desired fatigue life, hydraulic fluid pressures, and mechanical safety factors. In one example, one or more of the disclosed ranges of inter-pin dimension 132, stroke 222, rod eye diameter 252, trunnion cap hole diameter 242, diameter 328 of central axially extending bore 326 of tube 322, and outer diameter 334 of rod 332 of the present embodiment of the example boom cylinder may be directly and functionally associated with and established based on the presently disclosed hydraulic cylinder 26 for a boom 22 having an actuation system fluid pressure of 35,000 kPa ± 3500 kPa, which may facilitate improved and enhanced overall performance in accordance with any one or more of the disclosed embodiments of the present invention.

568LL arm hydraulic Cylinder (568 LL STICK CYLINDER) in an exemplary embodiment of a hydraulic Cylinder according to the present disclosure (such as a hydraulic Cylinder adapted for use as hydraulic Cylinder 32 for actuating arm 28 relative to boom 22), inter-pin dimension 132 of the hydraulic Cylinder may be equal to 2411 mm + -2.0 mm when rod 332, piston retention assembly 430, and piston 420 are fully retracted bottoming out at closed distal end 342 of tube 322. The stroke 222 for the example stick cylinder may be equal to 1661 mm 2.0 mm. The rod eye diameter 252 may be equal to 100mm ± 0.5 mm. The trunnion cap hole diameter 242 may be equal to 100mm + -0.5 mm. The diameter 328 of the central axially extending bore 326 of the example arm cylinder tube 322 may be equal to 180 mm 0.5 mm, and the outer diameter 334 of the example arm cylinder rod 332 may be equal to 130mm 0.5 mm. The system fluid pressure of the example stick cylinder may be equal to 35,000 kPa ± 3500 kPa. The disclosed size ranges are determined for a particular machine 10 based on one or more of: physics-based equations, finite element analysis, empirical evidence, and other computational analysis that take into account the following factors: such as the kinematic interrelationship between the boom and the stick on machine 10, the range of motion of the corresponding structural components, the loads that hydraulic rams will be subjected to during operation of machine 10, the expected fatigue life, hydraulic fluid pressures, and mechanical safety factors. In one example, one or more of the disclosed ranges of inter-pin dimension 132, stroke 222, stem eye diameter 252, trunnion cap hole diameter 242, diameter 328 of central axially extending bore 326 of tube 322, and outer diameter 334 of stem 332 of the present embodiment of the example stick cylinder may be directly and functionally associated with and established based on the presently disclosed hydraulic rams 32 for stick 28 having an actuation system fluid pressure of 35,000 kPa ± 3500 kPa, which may facilitate improved and enhanced overall performance in accordance with any one or more of the disclosed embodiments of the present invention.

M315NGH CR Boom-VA hydraulic Cylinder Boom (M315 NGH CR Boom-VA Cylinder Boom) in another exemplary embodiment of a hydraulic Cylinder according to the present disclosure, such as a hydraulic Cylinder adapted for use as hydraulic Cylinder 26 for actuating Boom 22, inter-pin dimension 132 of the hydraulic Cylinder may be equal to 1500 mm ± 2.0 mm when rod 332, piston retention assembly 430, and piston 420 bottom out at closed distal end 342 of tube 322 are fully retracted. The stroke 222 for the exemplary boom cylinder may be equal to 974 mm ± 2.0 mm. The rod eye diameter 252 may be equal to 80 mm ± 0.5 mm. The trunnion cap hole diameter 242 may be equal to 60 mm ± 0.5 mm. The diameter 328 of the central axially extending bore 326 of the example boom cylinder tube 322 may be equal to 105 mm 0.5 mm and the outer diameter 334 of the example boom cylinder rod 332 may be equal to 75 mm 0.5 mm. The system pressure of the example boom cylinder may be equal to 37,500 kPa ± 3750 kPa. The disclosed size ranges are determined for a particular machine based on one or more of: physics-based equations, finite element analysis, empirical evidence, and other data computational analysis that takes into account the following factors: such as the kinematic interrelationship between the boom and body of machine 10, the range of motion of the corresponding structural components, the loads to which the hydraulic rams will be subjected during operation of machine 10, the desired fatigue life, hydraulic fluid pressures, and mechanical safety factors. In one example, one or more of the disclosed ranges of inter-pin dimension 132, stroke 222, rod eye diameter 252, trunnion cap hole diameter 242, diameter 328 of tube 322 central axially extending bore 326, and outer diameter 334 of rod 332 of the present embodiment of the example boom cylinder may be directly and functionally associated with and established based on the presently disclosed hydraulic cylinder 26 for actuation of a boom 22 having a system pressure of 37,500 kPa ± 3750Pa, which may facilitate improved and enhanced overall performance in accordance with any one or more of the disclosed embodiments of the present invention.

M314 NGH Boom-1PC FA hydraulic Cylinder Boom (M314 NGH Boom-1PC FA Cylinder Boom) in another exemplary embodiment of a hydraulic Cylinder according to the present disclosure, such as a hydraulic Cylinder adapted for use as hydraulic Cylinder 26 for actuating Boom 22, the inter-pin dimension 132 of the hydraulic Cylinder may be equal to 1533 mm ± 2.0 mm when rod 332, piston retaining assembly 430, and piston 420 bottom out at closed distal end 342 of tube 322 are fully retracted. The stroke 222 for the exemplary boom cylinder may be equal to 912 mm 2.0 mm. The rod eye diameter 252 may be equal to 80 mm ± 0.5 mm. The trunnion cap hole diameter 242 may be equal to 60 mm ± 0.5 mm. The diameter 328 of the central axially extending bore 326 of the example boom cylinder tube 322 may be equal to 105 mm 0.5 mm and the outer diameter 334 of the example boom cylinder rod 332 may be equal to 75 mm 0.5 mm. The system pressure of the example boom cylinder may be equal to 37,500 kPa ± 3750 kPa. The disclosed size ranges are determined for a particular machine based on one or more of: physics-based equations, finite element analysis, empirical evidence, and other computational analysis that take into account the following factors: such as the kinematic interrelationship between the boom and body of the machine, the range of motion of the corresponding structural components, the loads to which the hydraulic rams will be subjected during machine operation, the expected fatigue life, hydraulic fluid pressures, and mechanical safety factors. In one example, one or more of the disclosed ranges of inter-pin dimension 132, stroke 222, rod eye diameter 252, trunnion cap hole diameter 242, diameter 328 of tube 322 central axially extending bore 326, and outer diameter 334 of rod 332 of the present embodiment of the example boom cylinder may be directly and functionally associated with and established based on the presently disclosed hydraulic cylinder 26 for a boom 22 having an actuation system pressure of 37,500 kPa ± 3750 kPa, which may facilitate improved and enhanced overall performance in accordance with any one or more of the disclosed embodiments of the present invention.

M314 NGH Boom-1PC hydraulic Cylinder Boom (M314 NGH Boom-1PC Cylinder liner Boom) in another exemplary embodiment of a hydraulic Cylinder according to the present disclosure, such as a hydraulic Cylinder suitable for use as hydraulic Cylinder 26 for actuating Boom 22, the inter-pin dimension 132 of the hydraulic Cylinder may be equal to 1533 mm ± 2.0 mm when rod 332, piston retention assembly 430, and piston 420 bottom out at closed distal end 342 of tube 322 are fully retracted. The stroke 222 for the example boom cylinder may be equal to 932 mm 2.0 mm. The rod eye diameter 252 may be equal to 80 mm ± 0.5 mm. The trunnion cap hole diameter 242 may be equal to 60 mm ± 0.5 mm. The diameter 328 of the central axially extending bore 326 of the example boom cylinder tube 322 may be equal to 105 mm 0.5 mm and the outer diameter 334 of the example boom cylinder rod 332 may be equal to 75 mm 0.5 mm. The system pressure of the example boom cylinder may be equal to 37,500 kPa ± 3750 kPa. The disclosed size ranges are determined for a particular machine based on one or more of: physics-based equations, finite element analysis, empirical evidence, and other computational analysis that take into account the following factors: such as the kinematic interrelationship between the boom and body of machine 10, the range of motion of the corresponding structural components, the loads to which the hydraulic rams will be subjected during operation of machine 10, the desired fatigue life, hydraulic fluid pressures, and mechanical safety factors. In one example, one or more of the disclosed ranges of inter-pin dimension 132, stroke 222, rod eye diameter 252, trunnion cap hole diameter 242, diameter 328 of tube 322 central axially extending bore 326, and outer diameter 334 of rod 332 of the present embodiment of the example boom cylinder may be directly and functionally associated with and established based on the presently disclosed hydraulic cylinder 26 for a boom 22 having an actuation system pressure of 37,500 kPa ± 3750 kPa, which may facilitate improved and enhanced overall performance in accordance with any one or more of the disclosed embodiments of the present invention.

M319NGH CR movable arm-VA CR hydraulic Cylinder BOOM (M319 NGH CRBoom-VA CR Cylinder BOOM) in another exemplary embodiment of a hydraulic Cylinder according to the present disclosure, such as a hydraulic Cylinder adapted for use as hydraulic Cylinder 26 for actuating BOOM 22, inter-pin dimension 132 of the hydraulic Cylinder may be equal to 1520 mm ± 2.0 mm when rod 332, piston retention assembly 430, and piston 420 bottom out at closed distal end 342 of tube 322 to fully retract. The stroke 222 for the example boom cylinder may be equal to 954 mm ± 2.0 mm. The rod eye diameter 252 may be equal to 90 mm ± 0.5 mm. The trunnion cap hole diameter 242 may be equal to 70mm ± 0.5 mm. The diameter 328 of the central axially extending bore 326 of the example boom cylinder tube 322 may be equal to 120 mm 0.5 mm and the outer diameter 334 of the example boom cylinder rod 332 may be equal to 85 mm 0.5 mm. The system pressure of the example boom cylinder may be equal to 37,500 kPa ± 3750 kPa. The disclosed size ranges are determined for a particular machine based on one or more of: physics-based equations, finite element analysis, empirical evidence, and other computational analysis that take into account the following factors: such as the kinematic interrelationship between the boom and body of the machine, the range of motion of the corresponding structural components, the loads to which the hydraulic rams will be subjected during operation of machine 10, the desired fatigue life, hydraulic fluid pressures, and mechanical safety factors. In one example, one or more of the disclosed ranges of the inter-pin dimension 132, the stroke 222, the rod eye diameter 252, the trunnion cap hole diameter 242, the diameter 328 of the central axially extending bore 326 of the tube 322, and the outer diameter 334 of the rod 332 of the present embodiment of the example boom cylinder may be directly and functionally associated with a pressure for the actuation system of 37,500 kPa + -3750 kPa of boom 22 is associated with, and may be established based on, the presently disclosed hydraulic cylinder 26, which may facilitate improved and enhanced performance in accordance with any one or more of the disclosed embodiments of the present disclosure.

M318NG Boom-1PC hydraulic Cylinder Boom (M318 NGH Boom-1PC Cylinder Boom) in another exemplary embodiment of a hydraulic Cylinder according to the present disclosure, such as a hydraulic Cylinder suitable for use as hydraulic Cylinder 26 for actuating Boom 22, the inter-pin dimension 132 of the hydraulic Cylinder may be equal to 1770 mm ± 2.0 mm when rod 332, piston retention assembly 430, and piston 420 bottom out at closed distal end 342 of tube 322 are fully retracted. The stroke 222 for the example boom cylinder may be equal to 893 mm 2.0 mm. The rod eye diameter 252 may be equal to 80 mm ± 0.5 mm. The trunnion cap hole diameter 242 may be equal to 70mm ± 0.5 mm. The diameter 328 of the central axially extending bore 326 of the example boom cylinder tube 322 may be equal to 120 mm 0.5 mm and the outer diameter 334 of the example boom cylinder rod 332 may be equal to 85 mm 0.5 mm. The system pressure of the example boom cylinder may be equal to 37,500 kPa ± 3750 kPa. The disclosed size ranges are determined for a particular machine 10 based on one or more of: physics-based equations, finite element analysis, empirical evidence, and other computational analysis that take into account the following factors: such as the kinematic interrelationship between the boom and body of machine 10, the range of motion of the corresponding structural components, the loads to which the hydraulic rams will be subjected during operation of machine 10, the desired fatigue life, hydraulic fluid pressures, and mechanical safety factors. In one example, one or more of the disclosed ranges of inter-pin dimension 132, stroke 222, rod eye diameter 252, trunnion cap hole diameter 242, diameter 328 of tube 322 central axially extending bore 326, and outer diameter 334 of rod 332 of the present embodiment of the example boom cylinder may be directly and functionally associated with and established based on the presently disclosed hydraulic cylinder 26 for a boom 22 having an actuation system pressure of 37,500 kPa ± 3750 kPa, which may facilitate improved and enhanced overall performance in accordance with any one or more of the disclosed embodiments of the present invention.

M317NGH CR Stick hydraulic Cylinder Stick (M317 NGH CR Stick Cylinder Stick) in an exemplary embodiment of a hydraulic Cylinder according to the present disclosure, such as a hydraulic Cylinder adapted for use as hydraulic Cylinder 32 for actuating Stick 28 relative to boom 22, the inter-pin dimension 132 of the hydraulic Cylinder may be equal to 1652 mm ± 2.0 mm when rod 332, piston retention assembly 430, and piston 420 bottom out at closed distal end 342 of tube 322 are fully retracted. The stroke 222 for the example arm cylinder may be equal to 1147 mm 2.0 mm. The rod eye diameter 252 may be equal to 70mm ± 0.5 mm. The trunnion cap hole diameter 242 may be equal to 70mm ± 0.5 mm. The diameter 328 of the central axially extending bore 326 of the example arm cylinder tube 322 may be equal to 115 mm 0.5 mm, and the outer diameter 334 of the example arm cylinder rod 332 may be equal to 80 mm 0.5 mm. The system pressure of the example stick cylinder may be equal to 37,500 kPa ± 3750 kPa. The disclosed size ranges are determined for a particular machine 10 based on one or more of: physics-based equations, finite element analysis, empirical evidence, and other computational analysis that take into account the following factors: such as the kinematic interrelationship between the boom and the stick on machine 10, the range of motion of the corresponding structural components, the loads that hydraulic rams will be subjected to during operation of machine 10, the expected fatigue life, hydraulic fluid pressures, and mechanical safety factors. In one example, one or more of the disclosed ranges of inter-pin dimension 132, stroke 222, rod eye diameter 252, trunnion cap hole diameter 242, diameter 328 of tube 322 central axially extending hole 326, and outer diameter 334 of rod 332 of this example stick cylinder embodiment may be directly and functionally associated with and may be established based on the presently disclosed hydraulic cylinder 32 for stick 28 with an actuation system pressure of 37,500 kPa ± 3750 kPa, which may facilitate improved and enhanced overall performance in accordance with any one or more of the disclosed embodiments of the utility model.

M317NGH CR Boom-VA CR hydraulic ram Boom (M317 NGH CR Boom-VA CR Cylinder Boom) in another exemplary embodiment of a hydraulic ram according to the present disclosure, such as a hydraulic ram adapted for use as hydraulic ram 26 for actuating Boom 22, an inter-pin dimension 132 of the hydraulic ram may be equal to 1520 mm ± 2.0 mm when rod 332, piston retention assembly 430, and piston 420 bottom out at closed distal end 342 of tube 322 are fully retracted. The stroke 222 for the example boom cylinder may be equal to 954 mm ± 0.5 mm. The rod eye diameter 252 may be equal to 90 mm ± 0.5 mm. The trunnion cap hole diameter 242 may be equal to 70mm ± 0.5 mm. The diameter 328 of the central axially extending bore 326 of the example boom cylinder tube 322 may be equal to 115 mm 0.5 mm and the outer diameter 334 of the example boom cylinder rod 332 may be equal to 80 mm 0.5 mm. The system pressure of the example boom cylinder may be equal to 37,500 kPa ± 3750 kPa. The disclosed size ranges are determined for a particular machine 10 based on one or more of: physics-based equations, finite element analysis, empirical evidence, and other computational analysis that take into account the following factors: such as the kinematic interrelationship between the boom and body of machine 10, the range of motion of the corresponding structural components, the loads to which the hydraulic rams will be subjected during operation of machine 10, the desired fatigue life, hydraulic fluid pressures, and mechanical safety factors. In one example, one or more of the disclosed ranges of inter-pin dimension 132, stroke 222, rod eye diameter 252, trunnion cap hole diameter 242, diameter 328 of tube 322 central axially extending bore 326, and outer diameter 334 of rod 332 of the present embodiment of the example boom cylinder may be directly and functionally associated with and established based on the presently disclosed hydraulic cylinder 26 for a boom 22 having an actuation system pressure of 37,500 kPa ± 3750 kPa, which may facilitate improved and enhanced overall performance in accordance with any one or more of the disclosed embodiments of the present invention.

M316NGH Boom-VA hydraulic ram Boom (M316 NGH Boom-VA Cylinder liner Boom) in another exemplary embodiment of a hydraulic ram according to the present disclosure, such as a hydraulic ram adapted for use as hydraulic ram 26 for actuating Boom 22, the inter-pin dimension 132 of the hydraulic ram may be equal to 1490 mm ± 2.0 mm when rod 332, piston retention assembly 430, and piston 420 bottom out at closed distal end 342 of tube 322 are fully retracted. The stroke 222 for the exemplary boom cylinder may be equal to 916 mm 2.0 mm. The rod eye diameter 252 may be equal to 90 mm ± 0.5 mm. The trunnion cap hole diameter 242 may be equal to 70mm ± 0.5 mm. The diameter 328 of the central axially extending bore 326 of the example boom cylinder tube 322 may be equal to 115 mm 2.0 mm and the outer diameter 334 of the example boom cylinder rod 332 may be equal to 80 mm 0.5 mm. The system pressure of the example boom cylinder may be equal to 37,500 kPa ± 3750 kPa. The disclosed size ranges are determined for a particular machine 10 based on one or more of: physics-based equations, finite element analysis, empirical evidence, and other computational analysis that take into account the following factors: such as the kinematic interrelationship between the boom and body of machine 10, the range of motion of the corresponding structural components, the loads to which the hydraulic rams will be subjected during operation of machine 10, the desired fatigue life, hydraulic fluid pressures, and mechanical safety factors. In one example, one or more of the disclosed ranges of inter-pin dimension 132, stroke 222, rod eye diameter 252, trunnion cap hole diameter 242, diameter 328 of tube 322 central axially extending bore 326, and outer diameter 334 of rod 332 of the present embodiment of the example boom cylinder may be directly and functionally associated with and established based on the presently disclosed hydraulic cylinder 26 for a boom 22 having an actuation system pressure of 37,500 kPa ± 3750 kPa, which may facilitate improved and enhanced performance in accordance with any one or more of the disclosed embodiments of the present invention.

M3022NGH/M3024NGH Boom-MH hydraulic ram Boom (M3022 NGH/M3024NGH Boom-MH Cylinder Boom) in another exemplary embodiment of a hydraulic ram according to the present disclosure, such as a hydraulic ram adapted for use as hydraulic ram 26 for actuating Boom 22, inter-pin dimension 132 of the hydraulic ram may be equal to 1517 mm ± 2.0 mm when rod 332, piston retention assembly 430, and piston 420 bottom out at closed distal end 342 of tube 322 are fully retracted. The stroke 222 for the exemplary boom cylinder may be equal to 983 mm ± 2.0 mm. The rod eye diameter 252 may be equal to 100mm ± 0.5 mm. The trunnion cap hole diameter 242 may be equal to 80 mm ± 0.5 mm. The diameter 328 of the central axially extending bore 326 of the example boom cylinder tube 322 may be equal to 130mm 0.5 mm and the outer diameter 334 of the example boom cylinder rod 332 may be equal to 90 mm 0.5 mm. The system pressure of the example boom cylinder may be equal to 37,500 kPa ± 3750 kPa. The disclosed size ranges are determined for a particular machine 10 based on one or more of: physics-based equations, finite element analysis, empirical evidence, and other computational analysis that take into account the following factors: such as the kinematic interrelationship between the boom and body of machine 10, the range of motion of the corresponding structural components, the loads to which the hydraulic rams will be subjected during operation of machine 10, the desired fatigue life, hydraulic fluid pressures, and mechanical safety factors. In one example, one or more of the disclosed ranges of inter-pin dimension 132, stroke 222, rod eye diameter 252, trunnion cap hole diameter 242, diameter 328 of tube 322 central axially extending bore 326, and outer diameter 334 of rod 332 of the present embodiment of the example boom cylinder may be directly and functionally associated with and established based on the presently disclosed hydraulic cylinder 26 for a boom 22 having an actuation system pressure of 37,500 kPa ± 3750 kPa, which may facilitate improved and enhanced overall performance in accordance with any one or more of the disclosed embodiments of the present invention.

M3022NGH/M3024NGH Stick MH Hydraulic ram Stick (M3022 NGH/M3024NGH Stick-MH Cylinder Stick) in an exemplary embodiment of a hydraulic ram according to the present disclosure, such as a hydraulic ram adapted for use as hydraulic ram 32 for actuating Stick 28 relative to boom 22, inter-pin dimension 132 of the hydraulic ram may be equal to 1733 mm + -2.0 mm when rod 332, piston retaining assembly 430, and piston 420 are bottomed out at closed distal end 342 of tube 322 to fully retract. The stroke 222 for this example arm cylinder may be equal to 1226 mm 2.0 mm. The rod eye diameter 252 may be equal to 90 mm ± 0.5 mm. The trunnion cap hole diameter 242 may be equal to 90 mm + -0.5 mm. The diameter 328 of the central axially extending bore 326 of the example arm cylinder tube 322 may be equal to 110 mm 0.5 mm, and the outer diameter 334 of the example arm cylinder rod 332 may be equal to 80 mm 0.5 mm. The system pressure of the example stick cylinder may be equal to 37,500 kPa ± 3750 kPa. The disclosed size ranges are determined for a particular machine 10 based on one or more of: physics-based equations, finite element analysis, empirical evidence, and other computational analysis that take into account the following factors: such as the kinematic interrelationship between the boom and the stick on machine 10, the range of motion of the corresponding structural components, the loads that hydraulic rams will be subjected to during operation of machine 10, the expected fatigue life, hydraulic fluid pressures, and mechanical safety factors. In one example, one or more of the disclosed ranges of inter-pin dimension 132, stroke 222, rod eye diameter 252, trunnion cap hole diameter 242, diameter 328 of central axially extending bore 326 of tube 322, and outer diameter 334 of rod 332 of the present embodiment of the example stick cylinder may be directly and functionally associated with and established based on the presently disclosed hydraulic cylinder 32 for stick 28 having an actuation system pressure of 37,500 kPa ± 3750 kPa, which may facilitate improved and enhanced overall performance in accordance with any one or more of the disclosed embodiments of the present invention.

M320NGH Boom-VA hydraulic Cylinder Boom (M320 NGH Boom-VA Cylinder Boom BOO) in another exemplary embodiment of a hydraulic Cylinder according to the present disclosure, such as a hydraulic Cylinder suitable for use as hydraulic Cylinder 26 for actuating Boom 22, the inter-pin dimension 132 of the hydraulic Cylinder may be equal to 1500 mm ± 2.0 mm when rod 332, piston retention assembly 430, and piston 420 bottom out at closed distal end 342 of tube 322 to fully retract. The stroke 222 for the example boom cylinder may be equal to 906 mm 2.0 mm. The rod eye diameter 252 may be equal to 100mm ± 0.5 mm. The trunnion cap hole diameter 242 may be equal to 80 mm ± 0.5 mm. The diameter 328 of the central axially extending bore 326 of the example boom cylinder tube 322 may be equal to 130mm 0.5 mm and the outer diameter 334 of the example boom cylinder rod 332 may be equal to 90 mm 0.5 mm. The system pressure of the example boom cylinder may be equal to 37,500 kPa ± 3750 kPa. The disclosed size ranges are determined for a particular machine 10 based on one or more of: physics-based equations, finite element analysis, empirical evidence, and other computational analysis that take into account the following factors: such as the kinematic interrelationship between the boom and body of machine 10, the range of motion of the corresponding structural components, the loads to which the hydraulic rams will be subjected during operation of machine 10, the desired fatigue life, hydraulic fluid pressures, and mechanical safety factors. In one example, one or more of the disclosed ranges of inter-pin dimension 132, stroke 222, rod eye diameter 252, trunnion cap hole diameter 242, diameter 328 of tube 322 central axially extending bore 326, and outer diameter 334 of rod 332 of the present embodiment of the example boom cylinder may be directly and functionally associated with and established based on the presently disclosed hydraulic cylinder 26 for a boom 22 having an actuation system pressure of 37,500 kPa ± 3750 kPa, which may facilitate improved and enhanced overall performance in accordance with any one or more of the disclosed embodiments of the present invention.

M320NGH Boom-1PC hydraulic Cylinder Boom (M320 NGH Boom-1PC Cylinder liner Boom) in another exemplary embodiment of a hydraulic Cylinder according to the present disclosure, such as a hydraulic Cylinder adapted for use as hydraulic Cylinder 26 for actuating Boom 22, the inter-pin dimension 132 of the hydraulic Cylinder may be equal to 1440 mm ± 2.0 mm when rod 332, piston retention assembly 430, and piston 420 bottom out at closed distal end 342 of tube 322 are fully retracted. The stroke 222 for the example boom cylinder may be equal to 906 mm 2.0 mm. The rod eye diameter 252 may be equal to 100mm ± 0.5 mm. The trunnion cap hole diameter 242 may be equal to 80 mm ± 0.5 mm. The diameter 328 of the central axially extending bore 326 of the example boom cylinder tube 322 may be equal to 130mm 0.5 mm and the outer diameter 334 of the example boom cylinder rod 332 may be equal to 90 mm 0.5 mm. The system pressure of the example boom cylinder may be equal to 37,500 kPa ± 3750 kPa. The disclosed size ranges are determined for a particular machine 10 based on one or more of: physics-based equations, finite element analysis, empirical evidence, and other computational analysis that take into account the following factors: such as the kinematic interrelationship between the boom and body of machine 10, the range of motion of the corresponding structural components, the loads to which the hydraulic rams will be subjected during operation of machine 10, the desired fatigue life, hydraulic fluid pressures, and mechanical safety factors. In one example, one or more of the disclosed ranges of inter-pin dimension 132, stroke 222, rod eye diameter 252, trunnion cap hole diameter 242, diameter 328 of tube 322 central axially extending bore 326, and outer diameter 334 of rod 332 of the present embodiment of the example boom cylinder may be directly and functionally associated with and established based on the presently disclosed hydraulic cylinder 26 for a boom 22 having an actuation system pressure of 37,500 kPa ± 3750 kPa, which may facilitate improved and enhanced overall performance in accordance with any one or more of the disclosed embodiments of the present invention.

M320NGH HAV hydraulic Cylinder (M320 NGH HAV Cylinder) in another exemplary embodiment of a hydraulic Cylinder according to the present disclosure, such as a hydraulic Cylinder adapted for use as hydraulic Cylinder 26 for actuating boom 22, the inter-pin dimension 132 of the hydraulic Cylinder may be equal to 1270 mm ± 2.0 mm when rod 332, piston retention assembly 430, and piston 420 bottom out at closed distal end 342 of tube 322 to fully retract. The stroke 222 for the example boom cylinder may be equal to 731 mm ± 2.0 mm. The rod eye diameter 252 may be equal to 110 mm ± 0.5 mm. The trunnion cap hole diameter 242 may be equal to 100mm + -0.5 mm. The diameter 328 of the central axially extending bore 326 of the example boom cylinder tube 322 may be equal to 160 mm 0.5 mm and the outer diameter 334 of the example boom cylinder rod 332 may be equal to 85 mm 0.5 mm. The system pressure of the example boom cylinder may be equal to 37,500 kPa ± 3750 kPa. The disclosed size ranges are determined for a particular machine 10 based on one or more of: physics-based equations, finite element analysis, empirical evidence, and other computational analysis that take into account the following factors: such as the kinematic interrelationship between the boom and body of machine 10, the range of motion of the corresponding structural components, the loads to which the hydraulic rams will be subjected during operation of machine 10, the desired fatigue life, hydraulic fluid pressures, and mechanical safety factors. In one example, one or more of the disclosed ranges of inter-pin dimension 132, stroke 222, rod eye diameter 252, trunnion cap hole diameter 242, diameter 328 of tube 322 central axially extending hole 326, and outer diameter 334 of rod 332 of the present embodiment of the example boom cylinder may be directly and functionally associated with and established based on the presently disclosed hydraulic cylinder 26 for a boom 22 having an actuation system pressure of 37,500 kPa ± 3750 kPa, which may result in improved performance in accordance with any one or more of the disclosed embodiments of the present invention.

M320NGH Stick-VA hydraulic ram (M320 NGH Stick-VA Cylinder) in another exemplary embodiment of a hydraulic ram disclosed in accordance with the present invention, such as a hydraulic ram adapted for use as hydraulic ram 32 for actuating Stick 28, the inter-pin dimension 132 of the hydraulic ram may be equal to 1775 mm ± 2.0 mm when rod 332, piston retention assembly 430, and piston 420 bottom out at closed distal end 342 of tube 322 are fully retracted. The stroke 222 for the example arm cylinder may be equal to 1205 mm 2.0 mm. The rod eye diameter 252 may be equal to 80 mm ± 0.5 mm. The trunnion cap hole diameter 242 may be equal to 80 mm ± 0.5 mm. The diameter 328 of the central axially extending bore 326 of the example arm cylinder tube 322 may be equal to 130mm 0.5 mm, and the outer diameter 334 of the example arm cylinder rod 332 may be equal to 90 mm 0.5 mm. The system pressure of the example stick cylinder may be equal to 37,500 kPa ± 3750 kPa. The disclosed size ranges are determined for a particular machine 10 based on one or more of: physics-based equations, finite element analysis, empirical evidence, and other computational analysis that take into account the following factors: such as the kinematic interrelationship between the stick and boom body of machine 10, the range of motion of the corresponding structural components, the loads to which the hydraulic rams will be subjected during operation of machine 10, the expected fatigue life, hydraulic fluid pressures, and mechanical safety factors. In one example, one or more of the disclosed ranges of inter-pin dimension 132, stroke 222, rod eye diameter 252, trunnion cap hole diameter 242, diameter 328 of tube 322 central axially extending bore 326, and outer diameter 334 of rod 332 of this example arm cylinder embodiment may be directly and functionally associated with and may be established based on the presently disclosed hydraulic rams 32 for an arm 28 having an actuation system pressure of 37,500 kPa ± 3750 kPa, which may result in improved performance in accordance with any one or more of the disclosed embodiments of the utility model.

M320NGH Stick-1PC hydraulic ram (M320 NGH Stick-1PC Cylinder) in another exemplary embodiment of a hydraulic ram according to the present disclosure, such as a hydraulic ram adapted for use as hydraulic ram 32 for actuating Stick 28, the inter-pin dimension 132 of the hydraulic ram may be equal to 1775 mm ± 2.0 mm when rod 332, piston retention assembly 430, and piston 420 bottom out at closed distal end 342 of tube 322 are fully retracted. The stroke 222 for the exemplary boom cylinder may be equal to 1205 mm ± 2.0 mm. The rod eye diameter 252 may be equal to 80 mm ± 0.5 mm. The trunnion cap hole diameter 242 may be equal to 80 mm ± 0.5 mm. The diameter 328 of the central axially extending bore 326 of the example arm cylinder tube 322 may be equal to 140 mm 0.5 mm, and the outer diameter 334 of the example arm cylinder rod 332 may be equal to 100mm 0.5 mm. The system pressure of the example stick cylinder may be equal to 37,500 kPa ± 3750 kPa. The disclosed size ranges are determined for a particular machine 10 based on one or more of: physics-based equations, finite element analysis, empirical evidence, and other computational analysis that take into account the following factors: such as the kinematic interrelationship between the boom and body of machine 10, the range of motion of the corresponding structural components, the loads to which the hydraulic rams will be subjected during operation of machine 10, the desired fatigue life, hydraulic fluid pressures, and mechanical safety factors. In one example, one or more of the disclosed ranges of inter-pin dimension 132, stroke 222, rod eye diameter 252, trunnion cap hole diameter 242, diameter 328 of central axially extending bore 326 of tube 322, and outer diameter 334 of rod 332 of the present embodiment of the example stick cylinder may be directly and functionally associated with and established based on the presently disclosed hydraulic cylinder 32 for stick 28 having an actuation system pressure of 37,500 kPa ± 3750 kPa, which may facilitate improved and enhanced overall performance in accordance with any one or more of the disclosed embodiments of the present invention.

M320NGH Bucket hydraulic ram (M320 NGH Bucket Cylinder) in another exemplary embodiment of a hydraulic ram according to the present disclosure, such as a hydraulic ram adapted for use as hydraulic ram 34 for actuating Bucket 14, the inter-pin dimension 132 of the hydraulic ram may be equal to 1624 mm ± 2.0 mm when rod 332, piston retention assembly 430, and piston 420 are fully retracted bottoming out at the closed distal end 342 of tube 322. The stroke 222 for the exemplary bucket cylinder may be equal to 1077 mm 2.0 mm. The rod eye diameter 252 may be equal to 80 mm ± 0.5 mm. The trunnion cap hole diameter 242 may be equal to 70mm ± 0.5 mm. The diameter 328 of the central axially extending bore 326 of the example boom cylinder tube 322 may be equal to 110 mm 0.5 mm and the outer diameter 334 of the example boom cylinder rod 332 may be equal to 80 mm 0.5 mm. The system pressure of the exemplary bucket cylinder may be equal to 37,500 kPa + -3750 kPa. The disclosed size ranges are determined for a particular machine 10 based on one or more of: physics-based equations, finite element analysis, empirical evidence, and other computational analysis that take into account the following factors: such as the kinematic interrelationship between the bucket and stick of machine 10, the range of motion of the respective structural components, the loads to which the hydraulic rams will be subjected during operation of machine 10, the expected fatigue life, hydraulic fluid pressures, and mechanical safety factors. In one example, one or more of the disclosed ranges of inter-pin dimension 132, stroke 222, rod eye diameter 252, trunnion cap hole diameter 242, diameter 328 of central axially extending bore 326 of tube 322, and outer diameter 334 of rod 332 of the present embodiment of the example bucket cylinder may be directly and functionally associated with and established based on the presently disclosed hydraulic rams 34 for actuating bucket 14 at 37,500 kPa ± 3750 kPa relative to system pressure, which may facilitate improved and enhanced overall performance in accordance with any one or more of the disclosed embodiments of the present invention.

MH3026NGH Boom-MH hydraulic ram (MH 3026NGH Boom-MH Cylinder) in another exemplary embodiment of a hydraulic ram according to the present disclosure, such as a hydraulic ram adapted for use as hydraulic ram 26 for actuating Boom 22, the inter-pin dimension 132 of the hydraulic ram may be equal to 1529 mm ± 2.0 mm when rod 332, piston retention assembly 430, and piston 420 bottom out at closed distal end 342 of tube 322 to fully retract. Stroke 222 for the exemplary boom cylinder may be equal to 967 mm 2.0 mm. The rod eye diameter 252 may be equal to 110 mm ± 0.5 mm. The trunnion cap hole diameter 242 may be equal to 80 mm ± 0.5 mm. The diameter 328 of the central axially extending bore 326 of the example boom cylinder tube 322 may be equal to 140 mm 0.5 mm and the outer diameter 334 of the example boom cylinder rod 332 may be equal to 100mm 0.5 mm. The system pressure of the example boom cylinder may be equal to 37,500 kPa ± 3750 kPa. The disclosed size ranges are determined for a particular machine 10 based on one or more of: physics-based equations, finite element analysis, empirical evidence, and other computational analysis that take into account the following factors: such as the kinematic interrelationship between the boom and body of machine 10, the range of motion of the corresponding structural components, the loads to which the hydraulic rams will be subjected during operation of machine 10, the desired fatigue life, hydraulic fluid pressures, and mechanical safety factors. In one example, one or more of the disclosed ranges of inter-pin dimension 132, stroke 222, rod eye diameter 252, trunnion cap hole diameter 242, diameter 328 of tube 322 central axially extending bore 326, and outer diameter 334 of rod 332 of the present embodiment of the example boom cylinder may be directly and functionally associated with and established based on the presently disclosed hydraulic cylinder 26 for a boom 22 having an actuation system pressure of 37,500 kPa ± 3750 kPa, which may facilitate improved and enhanced overall performance in accordance with any one or more of the disclosed embodiments of the present invention.

M3026NGH Stick-MH hydraulic ram (M3026 NGH Stick-MH Cylinder) in another exemplary embodiment of a hydraulic ram according to the present disclosure, such as a hydraulic ram adapted for use as hydraulic ram 32 for actuating Stick 28, the inter-pin dimension 132 of the hydraulic ram may be equal to 1834 mm ± 2.0 mm when rod 332, piston retention assembly 430 and piston 420 bottom out at the closed distal end 342 of tube 322 to fully retract. The stroke 222 for the example arm cylinder may be equal to 1305 mm 2.0 mm. The rod eye diameter 252 may be equal to 90 mm ± 0.5 mm. The trunnion cap hole diameter 242 may be equal to 90 mm + -0.5 mm. The diameter 328 of the central axially extending bore 326 of the example arm cylinder tube 322 may be equal to 120 mm 0.5 mm, and the outer diameter 334 of the example arm cylinder rod 332 may be equal to 85 mm 0.5 mm. The system pressure of the example stick cylinder may be equal to 37,500 kPa ± 3750 kPa. The disclosed size ranges are determined for a particular machine 10 based on one or more of: physics-based equations, finite element analysis, empirical evidence, and other computational analysis that take into account the following factors: such as the kinematic interrelationship between the boom and the stick of machine 10, the range of motion of the corresponding structural components, the loads to which the hydraulic rams will be subjected during operation of machine 10, the expected fatigue life, hydraulic fluid pressures, and mechanical safety factors. In one example, one or more of the disclosed ranges of inter-pin dimension 132, stroke 222, rod eye diameter 252, trunnion cap hole diameter 242, diameter 328 of tube 322 central axially extending bore 326, and outer diameter 334 of rod 332 of the present embodiment of the example stick cylinder may be directly and functionally associated with and established based on the presently disclosed hydraulic cylinder 32 for stick 28 with an actuation system pressure of 37,500 kPa ± 3750 kPa, which may facilitate improved and enhanced overall performance in accordance with any one or more of the embodiments disclosed herein.

M322NGH Boom-VA hydraulic Cylinder (M322 NGH Boom-VA Cylinder) in another exemplary embodiment of a hydraulic Cylinder according to the present disclosure, such as a hydraulic Cylinder adapted for use as hydraulic Cylinder 26 for actuating Boom 22, inter-pin dimension 132 of the hydraulic Cylinder may be equal to 1479 mm ± 2.0 mm when rod 332, piston retention assembly 430, and piston 420 bottom out at closed distal end 342 of tube 322 are fully retracted. The stroke 222 for the example boom cylinder may be equal to 862 mm ± 2.0 mm. The rod eye diameter 252 may be equal to 110 mm ± 0.5 mm. The trunnion cap hole diameter 242 may be equal to 80 mm ± 0.5 mm. The diameter 328 of the central axially extending bore 326 of the example boom cylinder tube 322 may be equal to 140 mm 0.5 mm and the outer diameter 334 of the example boom cylinder rod 332 may be equal to 100mm 0.5 mm. The system pressure of the example boom cylinder may be equal to 37,500 kPa ± 3750 kPa. The disclosed size ranges are determined for a particular machine 10 based on one or more of: physics-based equations, finite element analysis, empirical evidence, and other computational analysis that take into account the following factors: such as the kinematic interrelationship between the boom and body of machine 10, the range of motion of the corresponding structural components, the loads to which the hydraulic rams will be subjected during operation of machine 10, the desired fatigue life, hydraulic fluid pressures, and mechanical safety factors. In one example, one or more of the disclosed ranges of inter-pin dimension 132, stroke 222, rod eye diameter 252, trunnion cap hole diameter 242, diameter 328 of tube 322 central axially extending bore 326, and outer diameter 334 of rod 332 of the present embodiment of the example boom cylinder may be directly and functionally associated with and established based on the presently disclosed hydraulic cylinder 26 for a boom 22 having an actuation system pressure of 37,500 kPa ± 3750 kPa, which may facilitate improved and enhanced overall performance in accordance with any one or more of the disclosed embodiments of the present invention.

M322NGH HAV hydraulic Cylinder (M322 NGH HAV Cylinder) in another exemplary embodiment of a hydraulic Cylinder according to the present disclosure, such as a hydraulic Cylinder adapted for use as hydraulic Cylinder 26 for actuating boom 22, the inter-pin dimension 132 of the hydraulic Cylinder may be equal to 1255mm ± 2.0 mm when rod 332, piston retention assembly 430, and piston 420 are bottomed out at closed distal end 342 of tube 322 for full retraction. The stroke 222 for the example boom cylinder may be equal to 709mm ± 2.0 mm. The rod eye diameter 252 may be equal to 130mm ± 0.5 mm. The trunnion cap hole diameter 242 may be equal to 120 mm + -0.5 mm. The diameter 328 of the central axially extending bore 326 of the example boom cylinder tube 322 may be equal to 170mm 0.5 mm and the outer diameter 334 of the example boom cylinder rod 332 may be equal to 100mm 0.5 mm. The system pressure of the example boom cylinder may be equal to 37,500 kPa ± 3750 kPa. The disclosed size ranges are determined for a particular machine based on one or more of: physics-based equations, finite element analysis, empirical evidence, and other computational analysis that take into account the following factors: such as the kinematic interrelationship between the boom and body of the machine, the range of motion of the corresponding structural components, the loads to which the hydraulic rams will be subjected during machine operation, the expected fatigue life, hydraulic fluid pressures, and mechanical safety factors. In one example, one or more of the disclosed ranges of inter-pin dimension 132, stroke 222, rod eye diameter 252, trunnion cap hole diameter 242, diameter 328 of tube 322 central axially extending hole 326, and outer diameter 334 of rod 332 of the present embodiment of the example boom cylinder may be directly and functionally associated with and established based on the presently disclosed hydraulic cylinder 26 for a boom 22 having an actuation system pressure of 37,500 kPa ± 3750 kPa, which may result in improved performance in accordance with any one or more of the embodiments disclosed herein.

M322NGH stick hydraulic ram (M322 NGHStick Cylinder) in another exemplary embodiment of a hydraulic ram according to the present disclosure, such as a hydraulic ram adapted for use as hydraulic ram 32 for actuating stick 28, the inter-pin dimension 132 of the hydraulic ram may be equal to 1968 mm ± 2.0 mm when rod 332, piston retention assembly 430, and piston 420 are fully retracted bottoming out at closed distal end 342 of tube 322. The stroke 222 for the example arm cylinder may be equal to 1408 mm 2.0 mm. The rod eye diameter 252 may be equal to 80 mm ± 0.5 mm. The trunnion cap hole diameter 242 may be equal to 80 mm ± 0.5 mm. The diameter 328 of the central axially extending bore 326 of the example arm cylinder tube 322 may be equal to 140 mm 0.5 mm, and the outer diameter 334 of the example arm cylinder rod 332 may be equal to 100mm 0.5 mm. The system pressure of the example stick cylinder may be equal to 37,500 kPa ± 3750 kPa. The disclosed size ranges are determined for a particular machine 10 based on one or more of: physics-based equations, finite element analysis, empirical evidence, and other computational analysis that take into account the following factors: such as the kinematic interrelationship between the boom and the stick of machine 10, the range of motion of the corresponding structural components, the loads to which the hydraulic rams will be subjected during operation of machine 10, the expected fatigue life, hydraulic fluid pressures, and mechanical safety factors. In one example, one or more of the disclosed ranges of inter-pin dimension 132, stroke 222, rod eye diameter 252, trunnion cap hole diameter 242, diameter 328 of central axially extending bore 326 of tube 322, and outer diameter 334 of rod 332 of the present embodiment of the example stick cylinder may be directly and functionally associated with and established based on the presently disclosed hydraulic cylinder 32 for stick 28 having an actuation system pressure of 37,500 kPa ± 3750 kPa, which may facilitate improved and enhanced overall performance in accordance with any one or more of the disclosed embodiments of the present invention.

M322NGH Bucket hydraulic ram (M322 NGH Bucket Cylinder) in another exemplary embodiment of a hydraulic ram according to the present disclosure, such as a hydraulic ram adapted for use as hydraulic ram 34 for actuating Bucket 14, the inter-pin dimension 132 of the hydraulic ram may be equal to 1684 mm ± 2.0 mm when rod 332, piston retention assembly 430, and piston 420 are fully retracted bottoming out at the closed distal end 342 of tube 322. The stroke 222 for the exemplary bucket cylinder may be equal to 1104 mm 2.0 mm. The rod eye diameter 252 may be equal to 90 mm ± 0.5 mm. The trunnion cap hole diameter 242 may be equal to 70mm ± 0.5 mm. The diameter 328 of the central axially extending bore 326 of the example boom cylinder tube 322 may be equal to 120 mm 0.5 mm and the outer diameter 334 of the example boom cylinder rod 332 may be equal to 85 mm 0.5 mm. The system pressure of the exemplary bucket cylinder may be equal to 37,500 kPa + -3750 kPa. The disclosed size ranges are determined for a particular machine 10 based on one or more of: physics-based equations, finite element analysis, empirical evidence, and other computational analysis that take into account the following factors: such as the kinematic interrelationship between the bucket and stick of machine 10, the range of motion of the respective structural components, the loads to which the hydraulic rams will be subjected during operation of machine 10, the expected fatigue life, hydraulic fluid pressures, and mechanical safety factors. In one example, one or more of the disclosed ranges of inter-pin dimension 132, stroke 222, rod eye diameter 252, trunnion cap hole diameter 242, diameter 328 of central axially extending bore 326 of tube 322, and outer diameter 334 of rod 332 of the present embodiment of the example bucket cylinder may be directly and functionally associated with and established based on the presently disclosed hydraulic rams 34 for actuating bucket 14 at 37,500 kPa ± 3750 kPa relative to system pressure, which may facilitate improved and enhanced overall performance in accordance with any one or more of the disclosed embodiments of the present invention.

312 GX bucket rod Hydraulic Cylinder (312 GX Stick Cylinder) in another exemplary embodiment of a hydraulic Cylinder according to the present disclosure, such as a hydraulic Cylinder suitable for use as hydraulic Cylinder 32 for actuating bucket rod 28, the inter-pin dimension 132 of the hydraulic Cylinder may be equal to 1676 mm + -2.0 mm when rod 332, piston retaining assembly 430, and piston 420 are fully retracted bottoming out at the closed distal end 342 of tube 322. The stroke 222 for the example arm cylinder may be equal to 1194 mm ± 2.0 mm. The rod eye diameter 252 may be equal to 60 mm ± 0.5 mm. The trunnion cap hole diameter 242 may be equal to 60 mm ± 0.5 mm. The diameter 328 of the central axially extending bore 326 of the example arm cylinder tube 322 may be equal to 105 mm 0.5 mm, and the outer diameter 334 of the example arm cylinder rod 332 may be equal to 75 mm 0.5 mm. The system pressure of the example stick cylinder may be equal to 35,000 kPa ± 3500 kPa. The disclosed size ranges are determined for a particular machine 10 based on one or more of: physics-based equations, finite element analysis, empirical evidence, and other computational analysis that take into account the following factors: such as the kinematic interrelationship between the boom and the stick of machine 10, the range of motion of the corresponding structural components, the loads to which the hydraulic rams will be subjected during operation of machine 10, the expected fatigue life, hydraulic fluid pressures, and mechanical safety factors. In one example, one or more of the disclosed ranges of inter-pin dimension 132, stroke 222, stem eye diameter 252, trunnion cap hole diameter 242, diameter 328 of central axially extending bore 326 of tube 322, and outer diameter 334 of stem 332 of the present embodiment of the example stick cylinder may be directly and functionally associated with and established based on the presently disclosed hydraulic cylinder 32 for stick 28 having an actuation system pressure of 35,000 kPa ± 3500 kPa, which may facilitate improved and enhanced overall performance in accordance with any one or more of the disclosed embodiments of the present invention.

312 GX boom hydraulic ram (312 GXBoom Cylinder) in another exemplary embodiment of a hydraulic ram according to the present disclosure (such as a hydraulic ram adapted for use as hydraulic ram 26 for actuating boom 22), the inter-pin dimension 132 of the hydraulic ram may be equal to 1492 mm + -2.0 mm when rod 332, piston retention assembly 430, and piston 420 are fully retracted bottoming out at the closed distal end 342 of tube 322. The stroke 222 for the example boom cylinder may be equal to 1002 mm ± 2.0 mm. The rod eye diameter 252 may be equal to 80 mm ± 0.5 mm. The trunnion cap hole diameter 242 may be equal to 60 mm ± 0.5 mm. The diameter 328 of the central axially extending bore 326 of the example boom cylinder tube 322 may be equal to 95 mm 0.5 mm and the outer diameter 334 of the example boom cylinder rod 332 may be equal to 65 mm 0.5 mm. The system pressure of the example boom cylinder may be equal to 35,000 kPa ± 3750 kPa. The disclosed size ranges are determined for a particular machine 10 based on one or more of: physics-based equations, finite element analysis, empirical evidence, and other computational analysis that take into account the following factors: such as the kinematic interrelationship between the boom and body of the machine, the range of motion of the corresponding structural components, the loads to which the hydraulic rams will be subjected during operation of machine 10, the desired fatigue life, hydraulic fluid pressures, and mechanical safety factors. In one example, one or more of the disclosed ranges of inter-pin dimension 132, stroke 222, rod eye diameter 252, trunnion cap hole diameter 242, diameter 328 of tube 322 central axially extending bore 326, and outer diameter 334 of rod 332 of the present embodiment of the example boom cylinder may be directly and functionally associated with and established based on the presently disclosed hydraulic cylinder 26 for a boom 22 having an actuation system pressure of 35,000 kPa ± 3500 kPa, which may facilitate improved and enhanced overall performance in accordance with any one or more of the disclosed embodiments of the present invention.

312 GX bucket hydraulic ram (312 GXBucket Cylinder) in another exemplary embodiment of a hydraulic ram according to the present disclosure (such as a hydraulic ram adapted for use as hydraulic ram 34 for actuating bucket 14), when rod 332, piston retention assembly 430, and piston 420 are fully retracted bottoming out at closed distal end 342 of tube 322, the inter-pin dimension 132 of the hydraulic ram may be equal to 1392 mm + -2.0 mm. The stroke 222 for the exemplary bucket cylinder may be equal to 939 mm 2.0 mm. The rod eye diameter 252 may be equal to 70mm ± 0.5 mm. The trunnion cap hole diameter 242 may be equal to 60 mm ± 0.5 mm. The diameter 328 of the central axially extending bore 326 of the example boom cylinder tube 322 may be equal to 90 mm 0.5 mm and the outer diameter 334 of the example boom cylinder rod 332 may be equal to 65 mm 0.5 mm. The system pressure of the exemplary bucket cylinder may be equal to 35,000 kPa ± 3500 kPa. The disclosed size ranges are determined for a particular machine 10 based on one or more of: physics-based equations, finite element analysis, empirical evidence, and other computational analysis that take into account the following factors: such as the kinematic interrelationship between the bucket and stick of machine 10, the range of motion of the respective structural components, the loads to which the hydraulic rams will be subjected during operation of machine 10, the expected fatigue life, hydraulic fluid pressures, and mechanical safety factors. In one example, one or more of the disclosed ranges of inter-pin dimension 132, stroke 222, rod eye diameter 252, trunnion cap hole diameter 242, diameter 328 of central axially extending bore 326 of tube 322, and outer diameter 334 of rod 332 of the present embodiment of the example bucket cylinder may be directly and functionally associated with and established based on the presently disclosed hydraulic rams 34 for actuating bucket 14 at 35,000 kPa ± 3500 kPa relative to system pressure, which may facilitate improved and enhanced overall performance in accordance with any one or more of the disclosed embodiments of the present invention.

313 GX arm hydraulic ram (313 GX Stick Cylinder) in another exemplary embodiment of a hydraulic ram according to the present disclosure, such as a hydraulic ram adapted for use as hydraulic ram 32 for actuating arm 28, the inter-pin dimension 132 of the hydraulic ram may be equal to 1675 mm ± 2.0 mm when rod 332, piston retaining assembly 430, and piston 420 are fully retracted bottoming out at closed distal end 342 of tube 322. The stroke 222 for the example arm cylinder may be equal to 1197 mm 2.0 mm. The rod eye diameter 252 may be equal to 60 mm ± 0.5 mm. The trunnion cap hole diameter 242 may be equal to 60 mm ± 0.5 mm. The diameter 328 of the central axially extending bore 326 of the example arm cylinder tube 322 may be equal to 115 mm 0.5 mm, and the outer diameter 334 of the example arm cylinder rod 332 may be equal to 80 mm 0.5 mm. The system pressure of the example stick cylinder may be equal to 35,000 kPa ± 3500 kPa. The disclosed size ranges are determined for a particular machine 10 based on one or more of: physics-based equations, finite element analysis, empirical evidence, and other computational analysis that take into account the following factors: such as the kinematic interrelationship between the boom and the stick of machine 10, the range of motion of the corresponding structural components, the loads to which the hydraulic rams will be subjected during operation of machine 10, the expected fatigue life, hydraulic fluid pressures, and mechanical safety factors. In one example, one or more of the disclosed ranges of inter-pin dimension 132, stroke 222, stem eye diameter 252, trunnion cap hole diameter 242, diameter 328 of central axially extending bore 326 of tube 322, and outer diameter 334 of stem 332 of the present embodiment of the example stick cylinder may be directly and functionally associated with and established based on the presently disclosed hydraulic cylinder 32 for stick 28 having an actuation system pressure of 35,000 kPa ± 3500 kPa, which may facilitate improved and enhanced overall performance in accordance with any one or more of the disclosed embodiments of the present invention.

313 GX/316 GX Boom hydraulic Cylinder (313 GX/316 GX Boom Cylinder) in another exemplary embodiment of a hydraulic Cylinder according to the present disclosure, such as a hydraulic Cylinder suitable for use as hydraulic Cylinder 26 for actuating Boom 22, the inter-pin dimension 132 of the hydraulic Cylinder may be equal to 1505 mm ± 2.0 mm when rod 332, piston retention assembly 430, and piston 420 bottom out at closed distal end 342 of tube 322 to fully retract. The stroke 222 for the example boom cylinder may be equal to 1015 mm 2.0 mm. The rod eye diameter 252 may be equal to 80 mm ± 0.5 mm. The trunnion cap hole diameter 242 may be equal to 60 mm ± 0.5 mm. The diameter 328 of the central axially extending bore 326 of the example boom cylinder tube 322 may be equal to 105 mm 0.5 mm and the outer diameter 334 of the example boom cylinder rod 332 may be equal to 75 mm 0.5 mm. The system pressure of the example boom cylinder may be equal to 35,000 kPa ± 3750 kPa. The disclosed size ranges are determined for a particular machine 10 based on one or more of: physics-based equations, finite element analysis, empirical evidence, and other computational analysis that take into account the following factors: such as the kinematic interrelationship between the boom and body of machine 10, the range of motion of the corresponding structural components, the loads to which the hydraulic rams will be subjected during operation of machine 10, the desired fatigue life, hydraulic fluid pressures, and mechanical safety factors. In one example, one or more of the disclosed ranges of inter-pin dimension 132, stroke 222, rod eye diameter 252, trunnion cap hole diameter 242, diameter 328 of tube 322 central axially extending bore 326, and outer diameter 334 of rod 332 of the present embodiment of the example boom cylinder may be directly and functionally associated with and established based on the presently disclosed hydraulic cylinder 26 for a boom 22 having an actuation system pressure of 35,000 kPa ± 3500 kPa, which may facilitate improved and enhanced overall performance in accordance with any one or more of the disclosed embodiments of the present invention.

316 GX bucket rod hydraulic ram (316 GX Stick Cylinder) in another exemplary embodiment of a hydraulic ram according to the present disclosure, such as a hydraulic ram adapted for use as hydraulic ram 32 for actuating bucket rod 28, the inter-pin dimension 132 of the hydraulic ram may be equal to 1675 mm ± 2.0 mm when rod 332, piston retaining assembly 430, and piston 420 are fully retracted bottoming out at the closed distal end 342 of tube 322. The stroke 222 for the example arm cylinder may be equal to 1197 mm 2.0 mm. The rod eye diameter 252 may be equal to 60 mm ± 0.5 mm. The trunnion cap hole diameter 242 may be equal to 60 mm ± 0.5 mm. The diameter 328 of the central axially extending bore 326 of the example arm cylinder tube 322 may be equal to 120 mm 0.5 mm, and the outer diameter 334 of the example arm cylinder rod 332 may be equal to 85 mm 0.5 mm. The system pressure of the example stick cylinder may be equal to 35,000 kPa ± 3500 kPa. The disclosed size ranges are determined for a particular machine 10 based on one or more of: physics-based equations, finite element analysis, empirical evidence, and other computational analysis that take into account the following factors: such as the kinematic interrelationship between the boom and the stick of machine 10, the range of motion of the corresponding structural components, the loads to which the hydraulic rams will be subjected during operation of machine 10, the expected fatigue life, hydraulic fluid pressures, and mechanical safety factors. In one example, one or more of the disclosed ranges of inter-pin dimension 132, stroke 222, stem eye diameter 252, trunnion cap hole diameter 242, diameter 328 of central axially extending bore 326 of tube 322, and outer diameter 334 of stem 332 of the present embodiment of the example stick cylinder may be directly and functionally associated with and established based on the presently disclosed hydraulic cylinder 32 for stick 28 having an actuation system pressure of 35,000 kPa ± 3500 kPa, which may facilitate improved and enhanced overall performance in accordance with any one or more of the disclosed embodiments of the present invention.

316 GX Bucket hydraulic ram (316 GX Bucket Cylinder) in another exemplary embodiment of a hydraulic ram according to the present invention, such as a hydraulic ram adapted for use as hydraulic ram 34 for actuating Bucket 14, the inter-pin dimension 132 of the hydraulic ram may be equal to 1392 mm ± 2.0 mm when rod 332, piston retention assembly 430, and piston 420 are fully retracted bottoming out at closed distal end 342 of tube 322. The stroke 222 for the exemplary bucket cylinder may be equal to 939 mm 2.0 mm. The rod eye diameter 252 may be equal to 80 mm ± 0.5 mm. The trunnion cap hole diameter 242 may be equal to 60 mm ± 0.5 mm. The diameter 328 of the central axially extending bore 326 of the example boom cylinder tube 322 may be equal to 100mm 0.5 mm and the outer diameter 334 of the example boom cylinder rod 332 may be equal to 70mm 0.5 mm. The system pressure of the exemplary bucket cylinder may be equal to 35,000 kPa ± 3500 kPa. The disclosed size ranges are determined for a particular machine 10 based on one or more of: physics-based equations, finite element analysis, empirical evidence, and other computational analysis that take into account the following factors: such as the kinematic interrelationship between the bucket and stick of machine 10, the range of motion of the respective structural components, the loads to which the hydraulic rams will be subjected during operation of machine 10, the expected fatigue life, hydraulic fluid pressures, and mechanical safety factors. In one example, one or more of the disclosed ranges of inter-pin dimension 132, stroke 222, rod eye diameter 252, trunnion cap hole diameter 242, diameter 328 of central axially extending bore 326 of tube 322, and outer diameter 334 of rod 332 of the present embodiment of the example bucket cylinder may be directly and functionally associated with and established based on the presently disclosed hydraulic rams 34 for actuating bucket 14 at 35,000 kPa ± 3500 kPa relative to system pressure, which may facilitate improved and enhanced overall performance in accordance with any one or more of the disclosed embodiments of the present invention.

315NGH POB Stick hydraulic ram (315 NGH POB Stick Cylinder) in another exemplary embodiment of a hydraulic ram according to the present disclosure, such as a hydraulic ram adapted for use as hydraulic ram 32 for actuating Stick 28, the inter-pin dimension 132 of the hydraulic ram may be equal to 1332 mm ± 2.0 mm when rod 332, piston retention assembly 430, and piston 420 are fully retracted bottoming out at the closed distal end 342 of tube 322. The stroke 222 for the example arm cylinder may be equal to 948 mm 2.0 mm. The rod eye diameter 252 may be equal to 70mm ± 0.5 mm. The trunnion cap hole diameter 242 may be equal to 80 mm ± 0.5 mm (x 2 positions). The diameter 328 of the central axially extending bore 326 of the example arm cylinder tube 322 may be equal to 115 mm 0.5 mm, and the outer diameter 334 of the example arm cylinder rod 332 may be equal to 80 mm 0.5 mm. The system pressure of the example stick cylinder may be equal to 35,000 kPa ± 3500 kPa. The disclosed size ranges are determined for a particular machine 10 based on one or more of: physics-based equations, finite element analysis, empirical evidence, and other computational analysis that take into account the following factors: such as the kinematic interrelationship between the boom and the stick of machine 10, the range of motion of the corresponding structural components, the loads to which the hydraulic rams will be subjected during operation of machine 10, the expected fatigue life, hydraulic fluid pressures, and mechanical safety factors. In one example, one or more of the disclosed ranges of inter-pin dimension 132, stroke 222, stem eye diameter 252, trunnion cap hole diameter 242, diameter 328 of central axially extending bore 326 of tube 322, and outer diameter 334 of stem 332 of the present embodiment of the example stick cylinder may be directly and functionally associated with and established based on the presently disclosed hydraulic cylinder 32 for stick 28 having an actuation system pressure of 35,000 kPa ± 3500 kPa, which may facilitate improved and enhanced overall performance in accordance with any one or more of the disclosed embodiments of the present invention.

315NGH POB Boom hydraulic Cylinder (315 NGH POB Boom Cylinder) in another exemplary embodiment of a hydraulic Cylinder according to the present disclosure, such as a hydraulic Cylinder suitable for use as hydraulic Cylinder 26 for actuating Boom 22, inter-pin dimension 132 of the hydraulic Cylinder may be equal to 1469 mm ± 2.0 mm when rod 332, piston retention assembly 430, and piston 420 bottom out at closed distal end 342 of tube 322 to fully retract. The stroke 222 for the example boom cylinder may be equal to 1014mm 2.0 mm. The rod eye diameter 252 may be equal to 80 mm ± 0.5 mm. The trunnion cap hole diameter 242 may be equal to 60 mm ± 0.5 mm. The diameter 328 of the central axially extending bore 326 of the example boom cylinder tube 322 may be equal to 105 mm 0.5 mm and the outer diameter 334 of the example boom cylinder rod 332 may be equal to 75 mm 0.5 mm. The system pressure of the example boom cylinder may be equal to 35,000 kPa ± 3750 kPa. The disclosed size ranges are determined for a particular machine 10 based on one or more of: physics-based equations, finite element analysis, empirical evidence, and other computational analysis that take into account the following factors: such as the kinematic interrelationship between the boom and body of machine 10, the range of motion of the corresponding structural components, the loads to which the hydraulic rams will be subjected during operation of machine 10, the desired fatigue life, hydraulic fluid pressures, and mechanical safety factors. In one example, one or more of the disclosed ranges of inter-pin dimension 132, stroke 222, rod eye diameter 252, trunnion cap hole diameter 242, diameter 328 of tube 322 central axially extending bore 326, and outer diameter 334 of rod 332 of the present embodiment of the example boom cylinder may be directly and functionally associated with and established based on the presently disclosed hydraulic cylinder 26 for a boom 22 having an actuation system pressure of 35,000 kPa ± 3500 kPa, which may facilitate improved and enhanced overall performance in accordance with any one or more of the disclosed embodiments of the present invention.

315NGH POB hydraulic ram (315 NGH POB Cylinder) in another exemplary embodiment of a hydraulic ram according to the present disclosure, such as a hydraulic ram adapted for use as hydraulic ram 34 for actuating bucket 14, the inter-pin dimension 132 of the hydraulic ram may be equal to 900 mm ± 2.0 mm when rod 332, piston retention assembly 430, and piston 420 bottom out at closed distal end 342 of tube 322 are fully retracted. The stroke 222 for the exemplary bucket cylinder may be equal to 404 mm 2.0 mm. The rod eye diameter 252 may be equal to 80 mm ± 0.5 mm. The trunnion cap hole diameter 242 may be equal to 80 mm ± 0.5 mm. The diameter 328 of the central axially extending bore 326 of the example boom cylinder tube 322 may be equal to 120 mm 0.5 mm and the outer diameter 334 of the example boom cylinder rod 332 may be equal to 70mm 0.5 mm. The system pressure of the exemplary bucket cylinder may be equal to 35,000 kPa ± 3500 kPa. The disclosed size ranges are determined for a particular machine 10 based on one or more of: physics-based equations, finite element analysis, empirical evidence, and other computational analysis that take into account the following factors: such as the kinematic interrelationship between the bucket and stick of machine 10, the range of motion of the respective structural components, the loads to which the hydraulic rams will be subjected during machine operation, the expected fatigue life, hydraulic fluid pressures, and mechanical safety factors. In one example, one or more of the disclosed ranges of inter-pin dimension 132, stroke 222, rod eye diameter 252, trunnion cap hole diameter 242, diameter 328 of central axially extending bore 326 of tube 322, and outer diameter 334 of rod 332 of the present embodiment of the example bucket cylinder may be directly and functionally associated with and established based on the presently disclosed hydraulic rams 34 for actuating bucket 14 at 35,000 kPa ± 3500 kPa relative to system pressure, which may facilitate improved and enhanced overall performance in accordance with any one or more of the disclosed embodiments of the present invention.

313 NGH Stick hydraulic ram (313 NGH Stick Cylinder) in another exemplary embodiment of a hydraulic ram according to the present disclosure, such as a hydraulic ram adapted for use as hydraulic ram 32 for actuating Stick 28, the inter-pin dimension 132 of the hydraulic ram may be equal to 1637 mm ± 2.0 mm when rod 332, piston retention assembly 430, and piston 420 are fully retracted bottoming out at the closed distal end 342 of tube 322. The stroke 222 for the example arm cylinder may be equal to 1147 mm 2.0 mm. The rod eye diameter 252 may be equal to 70mm ± 0.5 mm. The trunnion cap hole diameter 242 may be equal to 70mm ± 0.5 mm. The diameter 328 of the central axially extending bore 326 of the example arm cylinder tube 322 may be equal to 115 mm 0.5 mm, and the outer diameter 334 of the example arm cylinder rod 332 may be equal to 80 mm 0.5 mm. The system pressure of the example stick cylinder may be equal to 35,000 kPa ± 3500 kPa. The disclosed size ranges are determined for a particular machine 10 based on one or more of: physics-based equations, finite element analysis, empirical evidence, and other computational analysis that take into account the following factors: such as the kinematic interrelationship between the boom and the stick of machine 10, the range of motion of the corresponding structural components, the loads to which the hydraulic rams will be subjected during operation of machine 10, the expected fatigue life, hydraulic fluid pressures, and mechanical safety factors. In one example, one or more of the disclosed ranges of inter-pin dimension 132, stroke 222, stem eye diameter 252, trunnion cap hole diameter 242, diameter 328 of central axially extending bore 326 of tube 322, and outer diameter 334 of stem 332 of the present embodiment of the example stick cylinder may be directly and functionally associated with and established based on the presently disclosed hydraulic cylinder 32 for stick 28 having an actuation system pressure of 35,000 kPa ± 3500 kPa, which may facilitate improved and enhanced overall performance in accordance with any one or more of the disclosed embodiments of the present invention.

313 NGH boom hydraulic cylinder (313 NGH Boom Cylinder) in another exemplary embodiment of a hydraulic Cylinder according to the present disclosure (such as a hydraulic Cylinder adapted for use as hydraulic Cylinder 26 for actuating Boom 22), inter-pin dimension 132 of the hydraulic Cylinder may be equal to 1544 mm ± 2.0 mm when rod 332, piston retention assembly 430, and piston 420 bottom out at closed distal end 342 of tube 322 are fully retracted. The stroke 222 for the exemplary boom cylinder may be equal to 1026 mm 2.0 mm. The rod eye diameter 252 may be equal to 80 mm ± 0.5 mm. The trunnion cap hole diameter 242 may be equal to 60 mm ± 0.5 mm. The diameter 328 of the central axially extending bore 326 of the example boom cylinder tube 322 may be equal to 105 mm 0.5 mm and the outer diameter 334 of the example boom cylinder rod 332 may be equal to 75 mm 0.5 mm. The system pressure of the example boom cylinder may be equal to 35,000 kPa ± 3750 kPa. The disclosed size ranges are determined for a particular machine 10 based on one or more of: physics-based equations, finite element analysis, empirical evidence, and other computational analysis that take into account the following factors: such as the kinematic interrelationship between the boom and body of machine 10, the range of motion of the corresponding structural components, the loads to which the hydraulic rams will be subjected during operation of machine 10, the expected fatigue life, the hydraulic fluid pressures, andand (5) mechanical safety factor. In one example, one or more of the disclosed ranges of inter-pin dimension 132, stroke 222, rod eye diameter 252, trunnion cap hole diameter 242, diameter 328 of tube 322 central axially extending bore 326, and outer diameter 334 of rod 332 of the present embodiment of the example boom cylinder may be directly and functionally associated with and established based on the presently disclosed hydraulic cylinder 26 for a boom 22 having an actuation system pressure of 35,000 kPa ± 3500 kPa, which may facilitate improved and enhanced overall performance in accordance with any one or more of the disclosed embodiments of the present invention.

313 NGH Bucket hydraulic ram (313 NGH Bucket Cylinder) in another exemplary embodiment of a hydraulic ram according to the present disclosure, such as a hydraulic ram adapted for use as hydraulic ram 34 for actuating Bucket 14, the inter-pin dimension 132 of the hydraulic ram may be equal to 1392 mm ± 2.0 mm when rod 332, piston retention assembly 430, and piston 420 bottom out at closed distal end 342 of tube 322 are fully retracted. The stroke 222 for the exemplary bucket cylinder may be equal to 939 mm 2.0 mm. The rod eye diameter 252 may be equal to 70mm ± 0.5 mm. The trunnion cap hole diameter 242 may be equal to 60 mm ± 0.5 mm. The diameter 328 of the central axially extending bore 326 of the example boom cylinder tube 322 may be equal to 95 mm 0.5 mm and the outer diameter 334 of the example boom cylinder rod 332 may be equal to 70mm 0.5 mm. The system pressure of the exemplary bucket cylinder may be equal to 35,000 kPa ± 3500 kPa. The disclosed size ranges are determined for a particular machine based on one or more of: physics-based equations, finite element analysis, empirical evidence, and other computational analysis that take into account the following factors: such as the kinematic interrelationship between the bucket and stick of machine 10, the range of motion of the respective structural components, the loads to which the hydraulic rams will be subjected during operation of machine 10, the expected fatigue life, hydraulic fluid pressures, and mechanical safety factors. In one example, one or more of the disclosed ranges of inter-pin dimension 132, stroke 222, rod eye diameter 252, trunnion cap hole diameter 242, diameter 328 of tube 322 central axially extending hole 326, and outer diameter 334 of rod 332 of the present embodiment of the example bucket cylinder may be directly and functionally associated with and established based on the presently disclosed hydraulic rams 34 for actuating bucket 14 at 35,000 kPa ± 3500 kPa relative to system pressure, which may facilitate improved and enhanced overall performance in accordance with any one or more of the embodiments disclosed herein.

313 NGH VAB Boom hydraulic Cylinder (313 NGH VAB Boom Cylinder) in another exemplary embodiment of a hydraulic Cylinder according to the present disclosure, such as a hydraulic Cylinder suitable for use as hydraulic Cylinder 26 for actuating variable angle Boom 22, the inter-pin dimension 132 of the hydraulic Cylinder may be equal to 1310 mm ± 2.0 mm when rod 332, piston retention assembly 430, and piston 420 bottom out at closed distal end 342 of tube 322 to fully retract. The stroke 222 for the exemplary boom cylinder may be equal to 865 mm ± 2.0 mm. The rod eye diameter 252 may be equal to 70mm ± 0.5 mm. The trunnion cap hole diameter 242 may be equal to 70mm ± 0.5 mm. The diameter 328 of the central axially extending bore 326 of the tube 322 of the example variable angle boom cylinder may be equal to 130mm 0.5 mm and the outer diameter 334 of the rod 332 of the example variable angle boom cylinder may be equal to 75 mm 0.5 mm. The system pressure of the example boom cylinder may be equal to 35,000 kPa ± 3500 kPa. The disclosed size ranges are determined for a particular machine 10 based on one or more of: physics-based equations, finite element analysis, empirical evidence, and other computational analysis that take into account the following factors: such as the kinematic interrelationship between the boom and body of machine 10, the range of motion of the corresponding structural components, the loads to which the hydraulic rams will be subjected during operation of machine 10, the desired fatigue life, hydraulic fluid pressures, and mechanical safety factors. In one example, one or more of the disclosed ranges of inter-pin dimension 132, stroke 222, rod eye diameter 252, trunnion cap hole diameter 242, diameter 328 of tube 322 central axially extending bore 326, and outer diameter 334 of rod 332 of this example variable angle boom cylinder embodiment may be directly and functionally associated with and established based on the presently disclosed hydraulic cylinder 26 for a boom 22 having an actuation system pressure of 35,000 kPa ± 3500 kPa, which may facilitate improved and enhanced overall performance in accordance with any one or more of the disclosed embodiments of the utility model.

315NGH Boom hydraulic Cylinder (315 NGH Boom Cylinder) in another exemplary embodiment of a hydraulic Cylinder according to the present disclosure, such as a hydraulic Cylinder adapted for use as hydraulic Cylinder 26 for actuating Boom 22, the inter-pin dimension 132 of the hydraulic Cylinder may be equal to 1523 mm ± 2.0 mm when rod 332, piston retention assembly 430, and piston 420 bottom out at closed distal end 342 of tube 322 are fully retracted. The stroke 222 for the example boom cylinder may be equal to 1023 mm ± 2.0 mm. The rod eye diameter 252 may be equal to 80 mm ± 0.5 mm. The trunnion cap hole diameter 242 may be equal to 60 mm ± 0.5 mm. The diameter 328 of the central axially extending bore 326 of the example boom cylinder tube 322 may be equal to 105 mm 0.5 mm and the outer diameter 334 of the example boom cylinder rod 332 may be equal to 75 mm 0.5 mm. The system pressure of the example boom cylinder may be equal to 35,000 kPa ± 3750 kPa. The disclosed size ranges are determined for a particular machine 10 based on one or more of: physics-based equations, finite element analysis, empirical evidence, and other computational analysis that take into account the following factors: such as the kinematic interrelationship between the boom and body of machine 10, the range of motion of the corresponding structural components, the loads to which the hydraulic rams will be subjected during operation of machine 10, the desired fatigue life, hydraulic fluid pressures, and mechanical safety factors. In one example, one or more of the disclosed ranges of inter-pin dimension 132, stroke 222, rod eye diameter 252, trunnion cap hole diameter 242, diameter 328 of tube 322 central axially extending bore 326, and outer diameter 334 of rod 332 of the present embodiment of the example boom cylinder may be directly and functionally associated with and established based on the presently disclosed hydraulic cylinder 26 for a boom 22 having an actuation system pressure of 35,000 kPa ± 3500 kPa, which may facilitate improved and enhanced overall performance in accordance with any one or more of the disclosed embodiments of the present invention.

317NGH Stick hydraulic ram (317 NGH Stick Cylinder) in another exemplary embodiment of a hydraulic ram according to the present disclosure, such as a hydraulic ram adapted for use as hydraulic ram 32 for actuating Stick 28, the interpoint dimension 132 of the hydraulic ram may be equal to 1827 mm ± 2.0 mm when rod 332, piston retention assembly 430, and piston 420 are fully retracted bottoming out at the closed distal end 342 of tube 322. The stroke 222 for the exemplary stick cylinder may be equal to 1331 mm 2.0 mm. The rod eye diameter 252 may be equal to 70mm ± 0.5 mm. The trunnion cap hole diameter 242 may be equal to 70mm ± 0.5 mm. The diameter 328 of the central axially extending bore 326 of the example arm cylinder tube 322 may be equal to 120 mm 0.5 mm, and the outer diameter 334 of the example arm cylinder rod 332 may be equal to 85 mm 0.5 mm. The system pressure of the example stick cylinder may be equal to 35,000 kPa ± 3500 kPa. The disclosed size ranges are determined for a particular machine 10 based on one or more of: physics-based equations, finite element analysis, empirical evidence, and other computational analysis that take into account the following factors: such as the kinematic interrelationship between the boom and the stick of machine 10, the range of motion of the corresponding structural components, the loads to which the hydraulic rams will be subjected during operation of machine 10, the expected fatigue life, hydraulic fluid pressures, and mechanical safety factors. In one example, one or more of the disclosed ranges of inter-pin dimension 132, stroke 222, stem eye diameter 252, trunnion cap hole diameter 242, diameter 328 of central axially extending bore 326 of tube 322, and outer diameter 334 of stem 332 of the present embodiment of the example stick cylinder may be directly and functionally associated with and established based on the presently disclosed hydraulic cylinder 32 for stick 28 having an actuation system pressure of 35,000 kPa ± 3500 kPa, which may facilitate improved and enhanced overall performance in accordance with any one or more of the disclosed embodiments of the present invention.

317NGH Boom hydraulic ram (317 NGH Boom Cylinder) in another exemplary embodiment of a hydraulic ram according to the present disclosure, such as a hydraulic ram adapted for use as hydraulic ram 26 for actuating Boom 22, the inter-pin dimension 132 of the hydraulic ram may be equal to 1693 mm ± 2.0 mm when rod 332, piston retention assembly 430, and piston 420 bottom out at closed distal end 342 of tube 322 are fully retracted. The stroke 222 for the exemplary boom cylinder may be equal to 1193 mm ± 2.0 mm. The rod eye diameter 252 may be equal to 80 mm ± 0.5 mm. The trunnion cap hole diameter 242 may be equal to 70mm ± 0.5 mm. The diameter 328 of the central axially extending bore 326 of the example boom cylinder tube 322 may be equal to 110 mm 0.5 mm and the outer diameter 334 of the example boom cylinder rod 332 may be equal to 80 mm 0.5 mm. The system pressure of the example boom cylinder may be equal to 35,000 kPa ± 3750 kPa. The disclosed size ranges are determined for a particular machine 10 based on one or more of: physics-based equations, finite element analysis, empirical evidence, and other computational analysis that take into account the following factors: such as the kinematic interrelationship between the boom and body of machine 10, the range of motion of the corresponding structural components, the loads to which the hydraulic rams will be subjected during operation of machine 10, the desired fatigue life, hydraulic fluid pressures, and mechanical safety factors. In one example, one or more of the disclosed ranges of inter-pin dimension 132, stroke 222, rod eye diameter 252, trunnion cap hole diameter 242, diameter 328 of tube 322 central axially extending bore 326, and outer diameter 334 of rod 332 of the present embodiment of the example boom cylinder may be directly and functionally associated with and established based on the presently disclosed hydraulic cylinder 26 for a boom 22 having an actuation system pressure of 35,000 kPa ± 3500 kPa, which may facilitate improved and enhanced overall performance in accordance with any one or more of the disclosed embodiments of the present invention.

317NGH Bucket hydraulic ram (317 NGH Bucket Cylinder) in another exemplary embodiment of a hydraulic ram according to the present disclosure, such as a hydraulic ram adapted for use as hydraulic ram 34 for actuating Bucket 14, the inter-pin dimension 132 of the hydraulic ram may be equal to 1559 mm ± 2.0 mm when rod 332, piston retention assembly 430, and piston 420 are fully retracted bottoming out at closed distal end 342 of tube 322. The stroke 222 for the exemplary bucket cylinder may be equal to 1039 mm 2.0 mm. The rod eye diameter 252 may be equal to 80 mm ± 0.5 mm. The trunnion cap hole diameter 242 may be equal to 70mm ± 0.5 mm. The diameter 328 of the central axially extending bore 326 of the example boom cylinder tube 322 may be equal to 105 mm 0.5 mm and the outer diameter 334 of the example boom cylinder rod 332 may be equal to 75 mm 0.5 mm. The system pressure of the exemplary bucket cylinder may be equal to 35,000 kPa ± 3500 kPa. The disclosed size ranges are determined for a particular machine 10 based on one or more of: physics-based equations, finite element analysis, empirical evidence, and other computational analysis that take into account the following factors: such as the kinematic interrelationship between the bucket and stick of machine 10, the range of motion of the respective structural components, the loads to which the hydraulic rams will be subjected during operation of machine 10, the expected fatigue life, hydraulic fluid pressures, and mechanical safety factors. In one example, one or more of the disclosed ranges of inter-pin dimension 132, stroke 222, rod eye diameter 252, trunnion cap hole diameter 242, diameter 328 of central axially extending bore 326 of tube 322, and outer diameter 334 of rod 332 of the present embodiment of the example bucket cylinder may be directly and functionally associated with and established based on the presently disclosed hydraulic rams 34 for actuating bucket 14 at 35,000 kPa ± 3500 kPa relative to system pressure, which may facilitate improved and enhanced overall performance in accordance with any one or more of the disclosed embodiments of the present invention.

317NGH VAB Boom hydraulic ram (317 NGH VAB Boom Cylinder) in another exemplary embodiment of a hydraulic ram according to the present disclosure, such as a hydraulic ram adapted for use as hydraulic ram 26 for actuating variable angle Boom 22, the inter-pin dimension 132 of the hydraulic ram may be equal to 1310 mm ± 2.0 mm when rod 332, piston retention assembly 430, and piston 420 bottom out at closed distal end 342 of tube 322 to fully retract. The stroke 222 for the exemplary boom cylinder may be equal to 865 mm ± 2.0 mm. The rod eye diameter 252 may be equal to 70mm ± 0.5 mm. The trunnion cap hole diameter 242 may be equal to 70mm ± 0.5 mm. The diameter 328 of the central axially extending bore 326 of the tube 322 of the example variable angle boom cylinder may be equal to 140 mm + -0.5 mm, and the outer diameter 334 of the rod 332 of the example variable angle boom cylinder may be equal to 85 mm + -0.5 mm. The system pressure of the example boom cylinder may be equal to 35,000 kPa ± 3500 kPa. The disclosed size ranges are determined for a particular machine 10 based on one or more of: physics-based equations, finite element analysis, empirical evidence, and other computational analysis that take into account the following factors: such as the kinematic interrelationship between the boom and body of machine 10, the range of motion of the corresponding structural components, the loads to which the hydraulic rams will be subjected during operation of machine 10, the desired fatigue life, hydraulic fluid pressures, and mechanical safety factors. In one example, one or more of the disclosed ranges of inter-pin dimension 132, stroke 222, rod eye diameter 252, trunnion cap hole diameter 242, diameter 328 of tube 322 central axially extending bore 326, and outer diameter 334 of rod 332 of this example variable angle boom cylinder embodiment may be directly and functionally associated with and established based on the presently disclosed hydraulic cylinder 26 for a boom 22 having an actuation system pressure of 35,000 kPa ± 3500 kPa, which may facilitate improved and enhanced overall performance in accordance with any one or more of the disclosed embodiments of the utility model.

320GX bucket rod hydraulic ram (320 gxsistk Cylinder) in another exemplary embodiment of a hydraulic ram according to the present disclosure, such as a hydraulic ram adapted for use as hydraulic ram 32 for actuating bucket rod 28, the inter-pin dimension 132 of the hydraulic ram may be equal to 2064 mm ± 2.0 mm when rod 332, piston retention assembly 430, and piston 420 are fully retracted bottoming out at closed distal end 342 of tube 322. The stroke 222 for the example arm cylinder may be equal to 1504 mm 2.0 mm. The rod eye diameter 252 may be equal to 80 mm ± 0.5 mm. The trunnion cap hole diameter 242 may be equal to 80 mm ± 0.5 mm. The diameter 328 of the central axially extending bore 326 of the example arm cylinder tube 322 may be equal to 135 mm 0.5 mm, and the outer diameter 334 of the example arm cylinder rod 332 may be equal to 95 mm 0.5 mm. The system pressure of the example stick cylinder may be equal to 35,000 kPa ± 3500 kPa. The disclosed size ranges are determined for a particular machine 10 based on one or more of: physics-based equations, finite element analysis, empirical evidence, and other computational analysis that take into account the following factors: such as the kinematic interrelationship between the boom and the stick of machine 10, the range of motion of the corresponding structural components, the loads to which the hydraulic rams will be subjected during operation of machine 10, the expected fatigue life, hydraulic fluid pressures, and mechanical safety factors. In one example, one or more of the disclosed ranges of inter-pin dimension 132, stroke 222, stem eye diameter 252, trunnion cap hole diameter 242, diameter 328 of central axially extending bore 326 of tube 322, and outer diameter 334 of stem 332 of the present embodiment of the example stick cylinder may be directly and functionally associated with and established based on the presently disclosed hydraulic cylinder 32 for stick 28 having an actuation system pressure of 35,000 kPa ± 3500 kPa, which may facilitate improved and enhanced overall performance in accordance with any one or more of the embodiments disclosed herein.

320GX Boom hydraulic Cylinder (320 GX Boom Cylinder) in another exemplary embodiment of a hydraulic Cylinder according to the present disclosure, such as a hydraulic Cylinder suitable for use as hydraulic Cylinder 26 for actuating Boom 22, the inter-pin dimension 132 of the hydraulic Cylinder may be equal to 1760 mm ± 2.0 mm when rod 332, piston retention assembly 430, and piston 420 bottom out at closed distal end 342 of tube 322 are fully retracted. The stroke 222 for the exemplary boom cylinder may be equal to 1260 mm ± 2.0 mm. The rod eye diameter 252 may be equal to 80 mm ± 0.5 mm. The trunnion cap hole diameter 242 may be equal to 80 mm ± 0.5 mm. The diameter 328 of the central axially extending bore 326 of the example boom cylinder tube 322 may be equal to 120 mm 0.5 mm and the outer diameter 334 of the example boom cylinder rod 332 may be equal to 85 mm 0.5 mm. The system pressure of the example boom cylinder may be equal to 35,000 kPa ± 3750 kPa. The disclosed size ranges are determined for a particular machine 10 based on one or more of: physics-based equations, finite element analysis, empirical evidence, and other computational analysis that take into account the following factors: such as the kinematic interrelationship between the boom and body of machine 10, the range of motion of the corresponding structural components, the loads to which the hydraulic rams will be subjected during operation of machine 10, the desired fatigue life, hydraulic fluid pressures, and mechanical safety factors. In one example, one or more of the disclosed ranges of inter-pin dimension 132, stroke 222, rod eye diameter 252, trunnion cap hole diameter 242, diameter 328 of tube 322 central axially extending bore 326, and outer diameter 334 of rod 332 of the present embodiment of the example boom cylinder may be directly and functionally associated with and established based on the presently disclosed hydraulic cylinder 26 for a boom 22 having an actuation system pressure of 35,000 kPa ± 3500 kPa, which may facilitate improved and enhanced overall performance in accordance with any one or more of the disclosed embodiments of the present invention.

320GX Bucket hydraulic ram (320 GX Bucket Cylinder) in another exemplary embodiment of a hydraulic ram according to the present disclosure, such as a hydraulic ram adapted for use as hydraulic ram 34 for actuating Bucket 14, the inter-pin dimension 132 of the hydraulic ram may be equal to 1684 mm ± 2.0 mm when rod 332, piston retention assembly 430, and piston 420 are fully retracted bottoming out at closed distal end 342 of tube 322. The stroke 222 for the exemplary bucket cylinder may be equal to 1104 mm 2.0 mm. The rod eye diameter 252 may be equal to 80 mm ± 0.5 mm. The trunnion cap hole diameter 242 may be equal to 70mm ± 0.5 mm. The diameter 328 of the central axially extending bore 326 of the example boom cylinder tube 322 may be equal to 115 mm 0.5 mm and the outer diameter 334 of the example boom cylinder rod 332 may be equal to 80 mm 0.5 mm. The system pressure of the exemplary bucket cylinder may be equal to 35,000 kPa ± 3500 kPa. The disclosed size ranges are determined for a particular machine 10 based on one or more of: physics-based equations, finite element analysis, empirical evidence, and other computational analysis that take into account the following factors: such as the kinematic interrelationship between the bucket and stick of machine 10, the range of motion of the respective structural components, the loads to which the hydraulic rams will be subjected during operation of machine 10, the expected fatigue life, hydraulic fluid pressures, and mechanical safety factors. In one example, one or more of the disclosed ranges of inter-pin dimension 132, stroke 222, rod eye diameter 252, trunnion cap hole diameter 242, diameter 328 of central axially extending bore 326 of tube 322, and outer diameter 334 of rod 332 of the present embodiment of the example bucket cylinder may be directly and functionally associated with and established based on the presently disclosed hydraulic rams 34 for actuating bucket 14 at 35,000 kPa ± 3500 kPa relative to system pressure, which may facilitate improved and enhanced overall performance in accordance with any one or more of the disclosed embodiments of the present invention.

323GX bucket rod hydraulic ram (323 GX Stick Cylinder) in another exemplary embodiment of a hydraulic ram according to the present disclosure, such as a hydraulic ram adapted for use as hydraulic ram 32 for actuating bucket rod 28, inter-pin dimension 132 of the hydraulic ram may be equal to 2064 mm ± 2.0 mm when rod 332, piston retention assembly 430, and piston 420 are fully retracted bottoming out at closed distal end 342 of tube 322. The stroke 222 for the example arm cylinder may be equal to 1504 mm 2.0 mm. The rod eye diameter 252 may be equal to 80 mm ± 0.5 mm. The trunnion cap hole diameter 242 may be equal to 80 mm ± 0.5 mm. The diameter 328 of the central axially extending bore 326 of the example arm cylinder tube 322 may be equal to 140 mm 0.5 mm, and the outer diameter 334 of the example arm cylinder rod 332 may be equal to 100mm 0.5 mm. The system pressure of the example stick cylinder may be equal to 35,000 kPa ± 3500 kPa. The disclosed size ranges are determined for a particular machine 10 based on one or more of: physics-based equations, finite element analysis, empirical evidence, and other computational analysis that take into account the following factors: such as the kinematic interrelationship between the boom and the stick of machine 10, the range of motion of the corresponding structural components, the loads to which the hydraulic rams will be subjected during operation of machine 10, the expected fatigue life, hydraulic fluid pressures, and mechanical safety factors. In one example, one or more of the disclosed ranges of inter-pin dimension 132, stroke 222, stem eye diameter 252, trunnion cap hole diameter 242, diameter 328 of central axially extending bore 326 of tube 322, and outer diameter 334 of stem 332 of the present embodiment of the example stick cylinder may be directly and functionally associated with and established based on the presently disclosed hydraulic cylinder 32 for stick 28 having an actuation system pressure of 35,000 kPa ± 3500 kPa, which may facilitate improved and enhanced overall performance in accordance with any one or more of the disclosed embodiments of the present invention.

323GX Boom hydraulic Cylinder (323 GX Boom Cylinder) in another exemplary embodiment of a hydraulic Cylinder according to the present disclosure, such as a hydraulic Cylinder suitable for use as hydraulic Cylinder 26 for actuating Boom 22, the inter-pin dimension 132 of the hydraulic Cylinder may be equal to 1760 mm ± 2.0 mm when rod 332, piston retention assembly 430, and piston 420 bottom out at closed distal end 342 of tube 322 are fully retracted. The stroke 222 for the exemplary boom cylinder may be equal to 1260 mm ± 2.0 mm. The rod eye diameter 252 may be equal to 80 mm ± 0.5 mm. The trunnion cap hole diameter 242 may be equal to 80 mm ± 0.5 mm. The diameter 328 of the central axially extending bore 326 of the example boom cylinder tube 322 may be equal to 120 mm 0.5 mm and the outer diameter 334 of the example boom cylinder rod 332 may be equal to 85 mm 0.5 mm. The system pressure of the example boom cylinder may be equal to 35,000 kPa ± 3750 kPa. The disclosed size ranges are determined for a particular machine 10 based on one or more of: physics-based equations, finite element analysis, empirical evidence, and other computational analysis that take into account the following factors: such as the kinematic interrelationship between the boom and body of machine 10, the range of motion of the corresponding structural components, the loads to which the hydraulic rams will be subjected during operation of machine 10, the desired fatigue life, hydraulic fluid pressures, and mechanical safety factors. In one example, one or more of the disclosed ranges of inter-pin dimension 132, stroke 222, rod eye diameter 252, trunnion cap hole diameter 242, diameter 328 of tube 322 central axially extending bore 326, and outer diameter 334 of rod 332 of the present embodiment of the example boom cylinder may be directly and functionally associated with and established based on the presently disclosed hydraulic cylinder 26 for a boom 22 having an actuation system pressure of 35,000 kPa ± 3500 kPa, which may facilitate improved and enhanced overall performance in accordance with any one or more of the disclosed embodiments of the present invention.

323GX Bucket hydraulic ram (323 GX Bucket Cylinder) in another exemplary embodiment of a hydraulic ram according to the present disclosure, such as a hydraulic ram adapted for use as hydraulic ram 34 for actuating Bucket 14, the inter-pin dimension 132 of the hydraulic ram may be equal to 1684 mm ± 2.0 mm when rod 332, piston retention assembly 430, and piston 420 are fully retracted bottoming out at closed distal end 342 of tube 322. The stroke 222 for the exemplary bucket cylinder may be equal to 1104 mm 2.0 mm. The rod eye diameter 252 may be equal to 80 mm ± 0.5 mm. The trunnion cap hole diameter 242 may be equal to 70mm ± 0.5 mm. The diameter 328 of the central axially extending bore 326 of the tube 322 of the example boom cylinder may be equal to 120 mm + -0.5 mm, and the outer diameter 334 of the rod 332 of the example bucket cylinder may be equal to 85 mm + -0.5 mm. The system pressure of the exemplary bucket cylinder may be equal to 35,000 kPa ± 3500 kPa. The disclosed size ranges are determined for a particular machine 10 based on one or more of: physics-based equations, finite element analysis, empirical evidence, and other computational analysis that take into account the following factors: such as the kinematic interrelationship between the bucket and stick of machine 10, the range of motion of the respective structural components, the loads to which the hydraulic rams will be subjected during operation of machine 10, the expected fatigue life, hydraulic fluid pressures, and mechanical safety factors. In one example, one or more of the disclosed ranges of inter-pin dimension 132, stroke 222, rod eye diameter 252, trunnion cap hole diameter 242, diameter 328 of central axially extending bore 326 of tube 322, and outer diameter 334 of rod 332 of the present embodiment of the example bucket cylinder may be directly and functionally associated with and established based on the presently disclosed hydraulic rams 34 for actuating bucket 14 at 35,000 kPa ± 3500 kPa relative to system pressure, which may facilitate improved and enhanced overall performance in accordance with any one or more of the disclosed embodiments of the present invention.

350 arm hydraulic ram (350 Stick Cylinder) in another exemplary embodiment of a hydraulic ram according to the present disclosure, such as a hydraulic ram adapted for use as hydraulic ram 32 for actuating arm 28, the inter-pin dimension 132 of the hydraulic ram may be equal to 2548 mm 2.0 mm when rod 332, piston retention assembly 430, and piston 420 are fully retracted bottoming out at closed distal end 342 of tube 322. The stroke 222 for this example arm cylinder may be equal to 1758 mm 2.0 mm. The rod eye diameter 252 may be equal to 100mm ± 0.5 mm. The trunnion cap hole diameter 242 may be equal to 100mm + -0.5 mm. The diameter 328 of the central axially extending bore 326 of the example arm cylinder tube 322 may be equal to 190 mm + -0.5 mm, and the outer diameter 334 of the example arm cylinder rod 332 may be equal to 130mm + -0.5 mm. The system pressure of the example stick cylinder may be equal to 35,000 kPa ± 3500 kPa. The disclosed size ranges are determined for a particular machine 10 based on one or more of: physics-based equations, finite element analysis, empirical evidence, and other computational analysis that take into account the following factors: such as the kinematic interrelationship between the boom and the stick of machine 10, the range of motion of the corresponding structural components, the loads to which the hydraulic rams will be subjected during operation of machine 10, the expected fatigue life, hydraulic fluid pressures, and mechanical safety factors. In one example, one or more of the disclosed ranges of inter-pin dimension 132, stroke 222, stem eye diameter 252, trunnion cap hole diameter 242, diameter 328 of central axially extending bore 326 of tube 322, and outer diameter 334 of stem 332 of this example stick cylinder embodiment may be directly and functionally associated with and may be established based on the presently disclosed hydraulic rams 32 for stick 28 having an actuation system pressure of 35,000 kPa ± 3500 kPa, which may facilitate improved and enhanced overall performance in accordance with any one or more of the disclosed embodiments of the present invention.

350 Boom hydraulic Cylinder (350 Boom Cylinder) in another exemplary embodiment of a hydraulic Cylinder according to the present disclosure, such as a hydraulic Cylinder adapted for use as hydraulic Cylinder 26 for actuating Boom 22, when rod 332, piston retention assembly 430, and piston 420 bottom out at closed distal end 342 of tube 322 to fully retract, inter-pin dimension 132 of the hydraulic Cylinder may be equal to 2247 mm ± 2.0 mm. The stroke 222 for the example boom cylinder may be equal to 1575 mm 2.0 mm. The rod eye diameter 252 may be equal to 110 mm ± 0.5 mm. The trunnion cap hole diameter 242 may be equal to 110 mm + -0.5 mm. The diameter 328 of the central axially extending bore 326 of the example boom cylinder tube 322 may be equal to 160 mm 0.5 mm and the outer diameter 334 of the example boom cylinder rod 332 may be equal to 110 mm 0.5 mm. The system pressure of the example boom cylinder may be equal to 35,000 kPa ± 3750 kPa. The disclosed size ranges are determined for a particular machine 10 based on one or more of: physics-based equations, finite element analysis, empirical evidence, and other computational analysis that take into account the following factors: such as the kinematic interrelationship between the boom and body of machine 10, the range of motion of the corresponding structural components, the loads to which the hydraulic rams will be subjected during operation of machine 10, the desired fatigue life, hydraulic fluid pressures, and mechanical safety factors. In one example, one or more of the disclosed ranges of inter-pin dimension 132, stroke 222, rod eye diameter 252, trunnion cap hole diameter 242, diameter 328 of tube 322 central axially extending bore 326, and outer diameter 334 of rod 332 of the present embodiment of the example boom cylinder may be directly and functionally associated with and established based on the presently disclosed hydraulic cylinder 26 for a boom 22 having an actuation system pressure of 35,000 kPa ± 3500 kPa, which may facilitate improved and enhanced overall performance in accordance with any one or more of the disclosed embodiments of the present invention.

350 Bucket TB Hydraulic Cylinder (350 Bucket TB Cylinder) in another exemplary embodiment of a hydraulic Cylinder according to the present disclosure, such as a hydraulic Cylinder suitable for use as hydraulic Cylinder 34 for actuating Bucket 14, the inter-pin dimension 132 of the hydraulic Cylinder may be equal to 2013 mm 2.0 mm when rod 332, piston retention assembly 430, and piston 420 are fully retracted bottoming out at the closed distal end 342 of tube 322. The stroke 222 for this exemplary bucket cylinder may be equal to 1356 mm 2.0 mm. The rod eye diameter 252 may be equal to 100mm ± 0.5 mm. The trunnion cap hole diameter 242 may be equal to 90 mm + -0.5 mm. The diameter 328 of the central axially extending bore 326 of the example boom cylinder tube 322 may be equal to 160 mm 0.5 mm and the outer diameter 334 of the example boom cylinder rod 332 may be equal to 110 mm 0.5 mm. The system pressure of the exemplary bucket cylinder may be equal to 35,000 kPa ± 3500 kPa. The disclosed size ranges are determined for a particular machine 10 based on one or more of: physics-based equations, finite element analysis, empirical evidence, and other computational analysis that take into account the following factors: such as the kinematic interrelationship between the bucket and stick of machine 10, the range of motion of the respective structural components, the loads to which the hydraulic rams will be subjected during operation of machine 10, the expected fatigue life, hydraulic fluid pressures, and mechanical safety factors. In one example, one or more of the disclosed ranges of inter-pin dimension 132, stroke 222, rod eye diameter 252, trunnion cap hole diameter 242, diameter 328 of central axially extending bore 326 of tube 322, and outer diameter 334 of rod 332 of the present embodiment of the example bucket cylinder may be directly and functionally associated with and established based on the presently disclosed hydraulic rams 34 for actuating bucket 14 at 35,000 kPa ± 3500 kPa relative to system pressure, which may facilitate improved and enhanced overall performance in accordance with any one or more of the disclosed embodiments of the present invention.

350 bucket UB Hydraulic ram (350 UB) in another exemplary embodiment of a hydraulic ram according to the present disclosure, such as a hydraulic ram adapted for use as hydraulic ram 34 for actuating bucket 14, the inter-pin dimension 132 of the hydraulic ram may be equal to 2089 mm + -2.0 mm when rod 332, piston retention assembly 430, and piston 420 bottom out at closed distal end 342 of tube 322 to fully retract. The stroke 222 for the exemplary bucket cylinder may be equal to 1396 mm 2.0 mm. The rod eye diameter 252 may be equal to 110 mm ± 0.5 mm. The trunnion cap hole diameter 242 may be equal to 100mm + -0.5 mm. The diameter 328 of the central axially extending bore 326 of the tube 322 of the example boom cylinder may be equal to 170mm 0.5 mm and the outer diameter 334 of the rod 332 of the example bucket cylinder may be equal to 110 mm 0.5 mm. The system pressure of the exemplary bucket cylinder may be equal to 35,000 kPa ± 3500 kPa. The disclosed size ranges are determined for a particular machine 10 based on one or more of: physics-based equations, finite element analysis, empirical evidence, and other computational analysis that take into account the following factors: such as the kinematic interrelationship between the bucket and stick of machine 10, the range of motion of the respective structural components, the loads to which the hydraulic rams will be subjected during operation of machine 10, the expected fatigue life, hydraulic fluid pressures, and mechanical safety factors. In one example, one or more of the disclosed ranges of inter-pin dimension 132, stroke 222, rod eye diameter 252, trunnion cap hole diameter 242, diameter 328 of central axially extending bore 326 of tube 322, and outer diameter 334 of rod 332 of the present embodiment of the example bucket cylinder may be directly and functionally associated with and established based on the presently disclosed hydraulic rams 34 for actuating bucket 14 at 35,000 kPa ± 3500 kPa relative to system pressure, which may facilitate improved and enhanced overall performance in accordance with any one or more of the disclosed embodiments of the present invention.

Industrial applicability

The disclosed hydraulic rams may be implemented on any machine where the application of specific performance dimensions for stroke, inter-pin length, rod eye pin diameter, trunnion cap pin diameter, nominal cylinder bore diameter, nominal piston rod diameter, and system pressure of hydraulic fluid supplied to each hydraulic ram is based at least in part on the results of: physics-based equations, finite element analysis, empirical data, structural analysis, and kinematic analysis of various structural elements of a particular machine (such as a boom, arm, and work tool of an excavator actuated relative to one another by hydraulic rams) required to perform certain tasks. The particular performance dimensions of each hydraulic ram used on a particular machine may be determined based at least in part on various computational analyses including fatigue analysis of the structural elements under load, link criteria, and kinematic considerations including the relative positions of the link points in which the head and rod ends of the hydraulic ram will be pivotally connected, hydraulic system pressures on various components of each hydraulic ram, hoop, torsional, shear, compressive, and tensile stresses, among other mechanical design considerations.

During operation of machine 10, an operator located within station 20 may command, via interface device 46, work tool 14 to move in a particular direction at a desired speed. One or more corresponding signals generated by interface device 46 may be provided to the electronic controller indicative of desired movement of structural components interconnected by one or more of the disclosed hydraulic rams, as well as machine performance information, such as sensor data including hydraulic fluid pressure data, position data, speed data, acceleration data, pump displacement data, and other data known in the art.

In response to the signals from interface device 46 and based on the machine performance information, the controller may generate control signals directed to the pumps, motors, and/or valves that control the flow of hydraulic fluid to the head end chamber on one side of each hydraulic ram and the flow of hydraulic fluid to the rod end chamber on the opposite side of the piston. In one exemplary embodiment, to cause right travel motor 42R to rotate in a first direction at an increased speed, the controller may generate control signals that cause the pump of the first circuit to increase its displacement and discharge fluid into the right pump passage at a greater rate. In addition, the controller may generate a control signal that moves the switching valve to one of the two flow-passing positions and/or holds it therein. After fluid from the right pump channel enters and passes through the right travel motor 42R, the fluid may return to the pump via the left pump channel. At this time, the speed of right travel motor 42R may depend on the discharge rate of the pump and on the amount of restriction (if any) to the flow of fluid through right travel motor 42R by the switching valve. By moving the switching valve to the other of the two flow-through positions, the movement of the right travel motor 42R can be reversed.

Hydraulic ram 32 may move simultaneously and/or independently of right travel motor 42R. Specifically, when right travel motor 42R receives fluid from the pump, one or more metering valves may be moved to transfer some fluid into head end chamber 352 or rod end chamber 354 of hydraulic rams 32. At the same time, each metering valve may be moved to direct waste fluid from hydraulic rams 32 back to the pump. When the switching valve and appropriate metering valve are fully open, the movement of right travel motor 42R and hydraulic ram 32 may be linked and dependent on the flow rate of fluid from the pump.

To provide independent control of the speed of right travel motor 42R and hydraulic ram 32, fluid flow to and/or from at least one of these actuators must be metered. For example, the switching valve and/or metering valve may be moved to an intermediate position, where fluid flow therethrough is restricted to some extent. When this occurs, the speed of one or both of the actuators may be adjusted as desired. The operation of hydraulic rams 26 and 34, as well as left travel motor 42L, swing motor 43, and auxiliary motors may be implemented in a similar manner as described above. Therefore, a detailed description of the single movements of these actuators will not be described in this disclosure.

During some operations, the flow rate of fluid provided to each actuator from its associated pump may be insufficient to meet operator demand. For example, during a boom raising operation by hydraulic rams 26, an operator may request a speed of machine 10 that will require a flow rate of fluid within the fourth circuit to exceed a capacity of the associated pump. During such a situation, the controller may, for example, cause the valve element of the corresponding combination valve to transfer fluid from the second hydraulic circuit to the fourth hydraulic circuit, thereby increasing the flow rate of fluid available to the hydraulic cylinder 26. At this time, fluid discharged from hydraulic rams 26 may be returned to the pumps of the fourth and second circuits via the combining valves. Flow sharing between other circuits via other combining valves may be implemented in a similar manner.

Fluid sharing between hydraulic circuits that direct fluid to a particular hydraulic ram or other actuator may be particularly beneficial due to situations where additional flow is required for a particular circuit. Specifically, during a digging operation, hydraulic rams 26 may require additional flow and, at the same time, the pump of the circuit that provides pressurized hydraulic fluid to the travel motor may be idle at this time. Thus, when the circuit supplying pressurized hydraulic fluid to the hydraulic rams is most needed, the full capacity (flow and pressure control) of the idle circuit is available. This may not always be the case for other circuits. For example, sharing fluid between non-idle circuits may be inefficient, have little benefit, and/or reduce control over circuit operation.

Flow sharing may also be selectively implemented when the amount of fluid discharged from one actuator exceeds the rate at which the corresponding pump can effectively consume return fluid. For example, during a boom 22 lowering operation, fluid may be drained from head end chamber 352 of hydraulic cylinder 26 at a high pressure as boom 22 moves under the force of gravity. Some of this exhaust fluid may be redirected back into rod end chamber 354 of hydraulic ram 26 via a metering valve. This operation may be referred to as regeneration and increases efficiency relative to directing fluid supplied by the pump into the rod end chamber 354. However, during regeneration, because there is a portion of the rod 332 in the rod end chamber 354, the amount of fluid displaced from the head end chamber 352 is greater than the amount of fluid entering the rod end chamber 354. Thus, this additional fluid that flows out of the head end chamber 352 must be consumed somewhere. In various exemplary embodiments, additional fluid discharged from hydraulic rams 26 during boom down movements may be directed through pumps associated with different circuits. This extra high pressure fluid may be used to drive the pump as a motor, thereby returning energy to the hydraulic system.

In the disclosed embodiments, the flow provided by the various pumps may be substantially unrestricted during many operations, such that a large amount of energy is not unnecessarily wasted during actuation. Accordingly, the disclosed embodiments may provide improved energy usage and savings. In addition, the ability to combine fluid flow from different circuits to meet the demands of each actuator may allow for a reduction in the number of pumps required within the hydraulic system and/or the size and capacity of these pumps. These reductions may reduce pump losses, increase overall efficiency, improve the volume and packaging of the hydraulic system, and/or reduce the cost of the hydraulic system. All of the considerations described above for sharing pressurized hydraulic fluid between certain hydraulic circuits on the machine and the hydraulic rams, and for regeneration when returning energy to the hydraulic system, may also be incorporated into the computational analysis used in determining the performance dimensions of each hydraulic ram, such as stroke dimension, inter-pin dimension, trunnion cap hole and trunnion pin diameter, and rod eye hole and rod eye pin diameter.

It will be apparent to those skilled in the art that various modifications and variations can be made to the disclosed system. Other embodiments will be apparent to those skilled in the art from consideration of the specification and practice of the disclosed system. It is intended that the specification and examples be considered as exemplary only, with a scope of protection determined by the following claims and their equivalents.

Claims

1. An actuator configured for actuating a first structural element on a machine relative to a second structural element on the machine, the actuator comprising:

a piston mounted at a distal end of the rod;

the diameter of the rod eye hole is equal to 130mm +/-0.5 mm;

the diameter of the trunnion cap hole is equal to 120 mm +/-0.5 mm;

the diameter of the rod is equal to 100mm plus or minus 0.5 mm.

2. The actuator of claim 1, wherein the pressure of the hydraulic fluid supplied to the actuator is 35,000 kPa ± 3,500 kPa.

3. The actuator of claim 2, wherein the machine is an excavator, the first structural element comprises a body of the excavator, and the second structural element comprises a boom of the excavator.

4. The actuator of claim 2, further comprising a damping assembly disposed at the closed distal end of the tube adjacent the distal end of the rod when the rod is fully retracted into the tube.

5. The actuator of claim 4, wherein the damping assembly axially protrudes from a radially intermediate portion of the closed distal end of the tube.

6. The actuator of claim 5, wherein the damping assembly is configured to be received within a mating blind formed in the distal end of the rod when the rod is fully retracted into the tube.

7. The actuator of claim 2, further comprising a damping assembly retained within a blind bore in the distal end of the rod, the damping assembly configured to enter a radially centered axial bore in the closed distal end of the tube when the rod is fully retracted into the tube.

8. The actuator of claim 2, further comprising an axial relief hole extending into the closed distal end of the tube, the axial relief hole extending parallel to and offset from a central axis of the tube, penetrating into the closed distal end of the tube, and intersecting a radially oriented relief hole extending between a pressure relief chamber defined in the distal end of the tube and an outer circumferential periphery of the tube.

9. The actuator of claim 2, wherein the head seal assembly is bolted to a rod end boss disposed at the proximal end of the tube.

10. A machine comprising a plurality of structural elements and a plurality of hydraulic actuators, each hydraulic actuator interconnecting two of said structural elements,

a piston mounted at a distal end of the rod;

the diameter of the rod eye hole is equal to 130mm +/-0.5 mm;

the diameter of the trunnion cap hole is equal to 120 mm +/-0.5 mm;

the diameter of the rod is equal to 100mm plus or minus 0.5 mm; and is